EP2229537A1 - Hydraulic drive device having two pressure chambers and method for operating a hydraulic drive device having two pressure chambers - Google Patents

Hydraulic drive device having two pressure chambers and method for operating a hydraulic drive device having two pressure chambers

Info

Publication number
EP2229537A1
EP2229537A1 EP10701488A EP10701488A EP2229537A1 EP 2229537 A1 EP2229537 A1 EP 2229537A1 EP 10701488 A EP10701488 A EP 10701488A EP 10701488 A EP10701488 A EP 10701488A EP 2229537 A1 EP2229537 A1 EP 2229537A1
Authority
EP
European Patent Office
Prior art keywords
piston
working
pressure
pressure chamber
drive device
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.)
Granted
Application number
EP10701488A
Other languages
German (de)
French (fr)
Other versions
EP2229537B1 (en
EP2229537B8 (en
Inventor
Erfindernennung liegt noch nicht vor Die
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
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Voith Patent GmbH
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Publication date
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Publication of EP2229537A1 publication Critical patent/EP2229537A1/en
Publication of EP2229537B1 publication Critical patent/EP2229537B1/en
Application granted granted Critical
Publication of EP2229537B8 publication Critical patent/EP2229537B8/en
Active legal-status Critical Current
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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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/204—Control means for piston speed or actuating force without external control, e.g. control valve inside the piston
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves
    • F15B13/0403—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool valves a secondary valve member sliding within the main spool, e.g. for regeneration flow
    • 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
    • F15B9/00—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member
    • F15B9/02—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type
    • F15B9/08—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor
    • F15B9/09—Servomotors with follow-up action, e.g. obtained by feed-back control, i.e. in which the position of the actuated member conforms with that of the controlling member with servomotors of the reciprocatable or oscillatable type controlled by valves affecting the fluid feed or the fluid outlet of the servomotor with electrical control means

Definitions

  • the invention relates to a hydraulic working device having a piston displaceably guided in a cylinder space along a working axis, which limits a working pressure chamber which can be pressurized with hydraulic fluid, furthermore with at least one partially guided in the piston between different control states control means for controlling the flow of hydraulic fluid from a high pressure supply in the working pressure chamber for moving the piston in the working direction and the working pressure chamber to a return space.
  • the invention also relates to a method for operating a hydraulic drive device, with a displaceably guided in a cylinder chamber piston which limits a working pressure chamber, wherein the working pressure chamber for moving the piston is pressurized in the working direction with hydraulic fluid.
  • Hydraulic drive devices and methods of the type mentioned are known in various designs.
  • a common feature in the prior art is that retraction and extension movements of the piston are effected by means of hydraulic fluid from a high-pressure supply.
  • Such devices are used in particular in stamping, embossing, nibbling, bending or forming machines. In this typically highly dynamic working operation, inherently high volume flows of the hydraulic fluid from the high-pressure supply occur, and sufficient energy must be provided. From DE 37 20 266 C2 and EP 0 296 104 B1 further hydraulic drive have become known.
  • the invention has for its object to enable an energy-saving hydraulic working operation, especially for use in stamping, embossing, nibbling, bending or forming machines.
  • This object is solved by a hydraulic drive device according to claim 1. It is therefore provided according to the invention that the working pressure chamber remote from the region of the piston defines a low pressure chamber which is pressurized during operation of the device by a low pressure supply for hydraulic fluid such that the piston is moved back against the working direction when the control means connects the working pressure chamber with the return chamber ,
  • the piston advantageously not only limits the working pressure chamber and the return chamber, but also a high-pressure chamber and a low-pressure chamber.
  • a pressurization of the working pressure chamber with hydraulic fluid causes a force on the piston in the working direction, while pressurization of the low-pressure chamber causes a force on the piston against the working direction.
  • the return chamber is connected in particular via a tank connection with a tank and serves to discharge the hydraulic fluid from the working pressure chamber.
  • the high-pressure chamber is connected in particular via a high-pressure connection to the high-pressure supply and serves to supply the working pressure chamber with hydraulic fluid.
  • the low-pressure space is connected in particular via a low-pressure connection to the low-pressure supply.
  • the high pressure chamber and the low pressure chamber are in particular so designed that when pressurized no resulting forces on the piston in or against the working direction
  • a further development of the invention provides that the low-pressure chamber is separated from the high-pressure supply independently of the control state of the control means.
  • the high-pressure supply is thus removed only during the working step (i.e., during the pre-driving) hydraulic fluid in which the piston is moved in the working direction by filling the working pressure chamber with hydraulic fluid. When the piston is moved back, no hydraulic fluid flows from the high pressure supply.
  • adjusting means are provided, by means of which the pressure of the high-pressure supply is adjustable depending on the travel of the piston and / or the workload of the piston.
  • the adjusting means are designed such that the
  • Pressure of the high-pressure supply for moving the piston from its retracted end position in the working direction until or until shortly before receiving a workload a value p1 and then, in particular during the workload, a value p2.
  • p1 is smaller than p2.
  • the adjusting means are advantageously designed such that upon further movement of the piston in the working direction after overcoming the workload, the pressure of the high pressure supply has a value p3, p3 is less than p2 and / or p3 is equal to p1.
  • High pressure source occurs only in the range of workload, for example, during the forming of a workpiece by the piston movement.
  • the ancestor of the piston to the onset of the workload is done with less energy.
  • a displacement measuring system for determining the travel path (i.e., the position) of the piston and / or a load measuring system for determining the working load of the piston is provided.
  • these measuring systems enable optimized high-pressure connection for further energy savings.
  • Control means in the region in which it is guided in the piston, limited along the working direction of a pressure chamber, which is pressure-connected to the low-pressure space.
  • control means is designed as a guided along the working axis spool, which is guided at least partially inside the piston, and which has control edges, which are designed to cooperate with further control edges on the piston to control the flow of hydraulic fluid into or out of the working pressure space.
  • control edges which are designed to cooperate with further control edges on the piston to control the flow of hydraulic fluid into or out of the working pressure space.
  • the spool may be formed integrally or in several parts, with individual parts of the spool can be connected to each other in particular via joints. As a result, in particular alignment errors can be compensated.
  • the spool can also on the one hand in the adjacent to the low-pressure chamber region of the piston in a cylindrical guide opening and on the other hand in the cylinder housing in a further cylindrical guide opening are guided, wherein the guide openings have the same diameter.
  • a coupling rod for actuating the spool is provided such that the spool can be pushed by means of the coupling rod in the direction of the piston. If the spool as described above defines a pressure chamber in the piston, which is pressure-connected to the low-pressure chamber, thus acting on the spool uninterrupted a force counter to the working direction. The coupling rod therefore has to push this to actuate the spool this only in the working direction, but not pull the spool. It is therefore not necessary that control rod and spool are firmly connected. In particular, the coupling rod can rest only loosely on the spool.
  • the coupling rod is connected to an electromechanical transducer.
  • the electromechanical transducer is designed as a linear direct motor and its longitudinal axis movable along the working rotor is firmly connected to the coupling rod.
  • a method with the features of claim 12 is also provided.
  • the working pressure chamber for moving the piston in the working direction with hydraulic fluid with a high pressure PH is applied.
  • a low-pressure space which is delimited by a region of the piston facing away from the working pressure chamber, is acted upon by a low-pressure PN to move the piston back against the working direction.
  • PN ⁇ PH.
  • the method can be further configured that the pressure of the working pressure chamber pressurizing hydraulic fluid is adjusted depending on the travel of the piston and / or the workload of the piston.
  • the low-pressure chamber is continuously applied with low pressure.
  • the high pressure of the working pressure chamber pressurizing hydraulic fluid for moving the piston from its retracted end position in the working direction until or shortly before receiving a workload a value p1 and then, in particular during the workload, a value p2 where p1 is less than p2.
  • the high pressure has a value p3, where p3 is less than p2 and / or p3 is equal to p1.
  • FIG. 1 shows a longitudinal section through a hydraulic drive device according to the invention in the rest position
  • FIG. 2 shows a part of the drive device according to FIG. 1 in the state for extending the piston as a longitudinal section
  • FIG. 3 shows a part of the drive device according to FIG. 1 in the state for returning the piston as a longitudinal section
  • Figure 4 shows the time course of the travel of the piston and the set pressure of the high pressure supply.
  • the hydraulic working device illustrated in FIGS. 1-3 has a cylinder 3 and a piston 5.
  • the piston 5 is displaceable and sealing in a cylinder chamber 8 along a working axis 10 guided.
  • the piston 5 is integrally connected to a piston rod 6, which projects beyond the cylinder 3 in a working direction 11.
  • the piston rod 6 may be connected to a punching tool (not shown) for forming a workpiece (not shown).
  • the piston 5 defines a working pressure chamber 13, a return chamber 15, a high pressure chamber 17 and a low pressure chamber 19, which are filled with hydraulic fluid for operating the device in the manner described below.
  • Pressurization of the working pressure chamber 13 with hydraulic fluid causes a force on the piston 5 in the working direction 11, while pressurization of the low-pressure chamber 19 causes a force on the piston 5 against the working direction 11.
  • the return chamber 15 is connected via a tank connection 16 with a tank 22 and serves to discharge the hydraulic fluid.
  • the high pressure chamber 17 is connected via a high pressure port 18 to a high pressure supply 24 for hydraulic fluid and serves to supply the working pressure chamber 13 with hydraulic fluid.
  • the low-pressure space 19 is connected via a low-pressure connection 20 to a low-pressure supply 26 for hydraulic fluid.
  • the piston 5 has a coaxial cylindrical bore 28 in which a control means 29 in the form of a spool 30 along the working axis 10 is guided longitudinally displaceable and sealing.
  • the axial end portions 32 and 34 of the spool 30 are formed like a piston.
  • the piston-side end portion 32 is sealingly guided in a cylindrical guide bore 36 in the piston 5 and limited in the piston 5 a pressure chamber 38 which is pressure-connected to the low-pressure chamber 19.
  • the piston 5 facing away from the end portion 34 of the spool 30 is sealingly guided in a cylindrical guide bore 40 in the cylinder 3.
  • the diameters of the guide bores 36 and 40 are the same size.
  • the spool 30 has through windows 48 with control edges 42 and 43. These are designed to cooperate with control edges 45 and 46 on the piston to a hydraulic follow-up control for piston. 5 and spool 30 to provide.
  • the return chamber 15 and the high-pressure chamber 17 have flow openings 41 and 44, which connect the return chamber 15 and the high-pressure chamber with the axial bore 28 for the spool 30.
  • the piston-side control edges 45 are in communication with the flow opening 41 and thus with the return chamber 15, the piston-side control edges 46 with the flow opening 44 and thus with the high pressure chamber 17.
  • the control edges 42 and 43 on the spool 30 have the same or a slightly smaller distance from each other By shifting the spool 30 along the working axis 10, consequently, the working pressure space 13 can be pressure-connected either to the return space 15 or to the high-pressure space 17.
  • the low-pressure chamber 19, regardless of the position of the spool 30 has no pressure connection to the high-pressure chamber 17 or to the return chamber 15.
  • a coupling rod 50 is provided, by means of which the spool 30 can be pushed in the direction of work 11.
  • the coupling rod 50 is only loosely on the piston-like end portion 34 of the spool 30 at.
  • the coupling rod 50 is firmly connected to the rotor 52 of an electromechanical converter 54, which is designed in particular as a linear direct motor.
  • adjustment means 60 are provided. These set the pressure of the high pressure supply 24 dependent on the travel, i. the position of the piston 5 along the working direction 11 a. The position of the piston 5 along the working axis 10 is determined via a displacement measuring system 62. Furthermore, it can be provided that the adjusting means 60 adjust the pressure of the high pressure supply 24 as a function of the working load of the piston 5, which are determined by means of a load measuring system (not shown).
  • the hydraulic drive device 1 operates in the manner described below.
  • the spool 30 is held by the coupling rod 50 in the rest position.
  • the force acting on the spool 30 by the low pressure in the pressure chamber 38 is counteracted counter to the working direction 11 by the control rod 50.
  • a flow of hydraulic fluid from the high pressure chamber 17 in the working pressure chamber 13 or the working pressure chamber 13 in the return chamber 15 is prevented, since the flow openings 41 and 44 are sealingly covered by the spool 30.
  • the coupling rod 50 pushes the spool 30 also in the working direction. As shown in Figure 2, thereby opening a gap between the control edges 43 on the spool 30 and the control edges 46 on the piston 5.
  • the high-pressure chamber 17 is pressure-connected to the working pressure chamber 13 and hydraulic fluid flows from the high-pressure supply 24 via the high-pressure chamber 17 through the passage window 48 in the working pressure chamber 13.
  • a force in the working direction 11 acts on the piston 5 and the piston 5 is moved in the working direction 11.
  • the piston 5 follows the movement of the spool 30 until the control edges 43 and 46 close again as shown in Figure 1, so that a flow of hydraulic fluid from the high-pressure chamber 17 is prevented in the working pressure chamber 13 or the working pressure chamber 13 in the return chamber 15. As a result, a rest position similar to the situation illustrated in FIG. 1 occurs again.
  • the high-pressure chamber 17 which is designed essentially as an annular space, extends so far in the axial direction that the high-pressure port 18 communicates with the flow opening 44 over the entire stroke. In operation, we also closed off by the spool 30 Flow opening 44 of the high-pressure chamber 17 is subjected to high pressure; however, a resultant force that moves the piston 5 in one direction does not result.
  • a hose connection between the high-pressure connection 18 and the flow-through opening 44 could also be provided.
  • the coupling rod 50 is moved by the linear direct motor 54 against the working direction of the end portion 34 of the spool 30 away. Due to the pressure prevailing in the pressure chamber 38 low pressure of the spool 30 is moved counter to the working direction 11. As shown in Figure 3, thereby opens a gap between the control edges 42 on the spool 30 and the control edges 45 on the piston 5, so that the working pressure chamber 13 is pressure-connected to the return chamber 15. Due to the low pressure prevailing in the low pressure chamber 19, a force counteracts the working direction 11 on the piston 5. The piston 5 can now move counter to the working direction 11, wherein the hydraulic fluid located in the working pressure chamber 13 through the passage window 48 in the return chamber 15 and there is displaced into the tank 22.
  • the piston 5 and the spool 30 move so long against the working direction 11 until further movement of the spool 30 is prevented by abutment of the end portion 34 of the spool 30 to the coupling rod 50. Then, the spool shifts back into a position in which the gap between the control edges 42 and 45 is closed. It turns then again a rest position similar to the figure 1 shown rest position.
  • the full working force of the piston 5 in the working direction 11 is not during the entire working cycle from forward and backward travel of the piston 5 is required. Rather, the full working force is only required when striking a piston rod 6 connected to the punching tool (not shown) on a workpiece (not shown) and during the penetration of the workpiece.
  • the adjusting means 60 adjust the pressure of the high pressure supply 24 depending on the travel path, ie from the position of the piston 5.
  • FIG. 4 shows the time characteristic of the position of the piston 5 together with the time course of the pressure of the high-pressure supply 24 set by the adjusting means 60.
  • the piston 5 is moved in the working direction 11 up to the position POS1, in which the punching tool connected to the piston rod strikes the workpiece to be deformed.
  • the pressure of the high pressure supply 24 is set to a low value p1, which may be selected to be equal to that of the low pressure supply 26 in particular.
  • the travel is detected by the displacement measuring system 62 and compared with a preset value, which corresponds for example to the distance of the punching tool in retracted end position of the piston 5 to the workpiece. If the piston has moved over the specified distance, then the punch meets the workpiece to be deformed. This takes place at the position of the piston indicated by POS1 in FIG.
  • the adjusting means 60 increase the pressure of the high-pressure supply 24 to a value p2, which is significantly higher than p1 and typically corresponds to the maximum pressure of the high-pressure supply 24. This high pressure is maintained for the further movement of the piston 5 in the working direction 11 until the punching tool attached to the piston rod 6 has penetrated the workpiece (position POS2 of the piston 5 in FIG. 4). Thus, the workload on the piston 5 decreases. If further movement of the piston 5 in working direction 11 to the position POS3 is provided, the adjusting means 60 reduce the pressure of the high-pressure supply 24 to a value p3 which is smaller than the pressure p2 and in particular equal to the pressure of the low-pressure supply 26.
  • the described embodiment of the invention reduces the energy consumption in typical use with repeated extension and retraction of the piston 5 considerably. This is done on the one hand in that the return movement of the piston 5 against the working direction 11 is basically caused by hydraulic fluid from an energy-saving low-pressure supply 26. On the other hand, the energy requirement is further reduced by the described, depending on the travel and / or the workload of the piston 5 high-pressure connection of the high-pressure supply 24.

Abstract

The invention relates to a hydraulic drive device, comprising a piston which is guided displaceably in a cylinder chamber along a working axis and adjoins a working pressure chamber that can be pressurized by hydraulic fluid, and comprising a control means that is guided in the piston at least in some sections between different control states in order to control the flow of the hydraulic fluid from a high pressure supply into the working pressure chamber to move the piston in the working direction and from the working pressure chamber to a return flow chamber, wherein the region of the piston facing away from the working pressure chamber delimits a low pressure chamber that is pressurized by a low pressure supply for hydraulic fluid during the operation of the device such that the piston is moved back against the working direction when the control means connects the working pressure chamber to the return flow chamber. The invention furthermore relates to a method for operating a hydraulic drive device.

Description

Titel: Hydraulische Antriebsvorrichtung mit zwei Druckräumen und Verfahren zum Betreiben einer hydraulischen Antriebsvorrichtung mit zwei Druckräumen [0001] Die Erfindung betrifft eine hydraulische Arbeitsvorrichtung mit einem in einem Zylinderraum längs einer Arbeitsachse verschiebbar geführten Kolben, der einen mit Hydraulikflüssigkeit druckbeaufschlagbaren Arbeitsdruckraum begrenzt, ferner mit einem wenigstens abschnittsweise im Kolben zwischen verschiedenen Steuerzuständen geführten Steuermittel zur Steuerung des Durchflusses der Hydraulikflüssigkeit von einer Hochdruckversorgung in den Arbeitsdruckraum zum Bewegen des Kolbens in Arbeitsrichtung und vom Arbeitsdruckraum zu einem Rücklaufraum. Die Erfindung bezieht sich außerdem auf ein Verfahren zum Betrieb einer hydraulischen Antriebsvorrichtung, mit einem in einem Zylinderraum verschiebbar geführten Kolben, welcher einen Arbeitsdruckraum begrenzt, wobei der Arbeitsdruckraum zum Bewegen des Kolbens in Arbeitsrichtung mit Hydraulikflüssigkeit druckbeaufschlagt wird. Title: Hydraulic drive device with two pressure chambers and method for operating a hydraulic drive device with two pressure chambers. The invention relates to a hydraulic working device having a piston displaceably guided in a cylinder space along a working axis, which limits a working pressure chamber which can be pressurized with hydraulic fluid, furthermore with at least one partially guided in the piston between different control states control means for controlling the flow of hydraulic fluid from a high pressure supply in the working pressure chamber for moving the piston in the working direction and the working pressure chamber to a return space. The invention also relates to a method for operating a hydraulic drive device, with a displaceably guided in a cylinder chamber piston which limits a working pressure chamber, wherein the working pressure chamber for moving the piston is pressurized in the working direction with hydraulic fluid.
[0002] Hydraulische Antriebsvorrichtungen und Verfahren der genannten Art sind in verschiedenen Ausführungen bekannt. Insoweit wird zum Stand der Technik beispielsweise auf die EP 0 296 104 B1 verwiesen. Gemeinsames Merkmal im Stand der Technik ist, dass Ein- und Ausfahrbewegungen des Kolbens mittels Hydraulikflüssigkeit von einer Hochdruckversorgung bewirkt werden. Derartige Vorrichtungen finden insbesondere bei Stanz-, Präge-, Nibbel-, Biege- oder Umformmaschinen Verwendung. Bei diesem typischerweise hochdynamischen Arbeitsbetrieb treten prinzipbedingt hohe Volumenströme der Hydraulikflüssigkeit von der Hochdruckversorgung auf, und es muss ausreichend Energie bereitgestellt werden. [0003] Aus der DE 37 20 266C2 und der EP 0 296 104 B1 sind weitere hydraulische Antrieb bekannt geworden.Hydraulic drive devices and methods of the type mentioned are known in various designs. In that regard, reference is made to the state of the art, for example, to EP 0 296 104 B1. A common feature in the prior art is that retraction and extension movements of the piston are effected by means of hydraulic fluid from a high-pressure supply. Such devices are used in particular in stamping, embossing, nibbling, bending or forming machines. In this typically highly dynamic working operation, inherently high volume flows of the hydraulic fluid from the high-pressure supply occur, and sufficient energy must be provided. From DE 37 20 266 C2 and EP 0 296 104 B1 further hydraulic drive have become known.
[0004] Der Erfindung liegt die Aufgabe zugrunde, einen energiesparenden hydraulischen Arbeitsbetrieb, insbesondere für den Einsatz in Stanz-, Präge-, Nibbel-, Biege- oder Umformmaschinen zu ermöglichen. [0005] Diese Aufgabe wird durch eine hydraulische Antriebsvorrichtung nach Anspruch 1 gelöst. Es ist demnach erfindungsgemäß vorgesehen, dass der dem Arbeitsdruckraum abgewandte Bereich des Kolbens einen Niederdruckraum begrenzt, der im Betrieb der Vorrichtung von einer Niederdruckversorgung für Hydraulikflüssigkeit derart druckbeaufschlagt ist, dass der Kolben entgegen der Arbeitsrichtung rückbewegt wird, wenn das Steuermittel den Arbeitsdruckraum mit dem Rücklaufraum verbindet.The invention has for its object to enable an energy-saving hydraulic working operation, especially for use in stamping, embossing, nibbling, bending or forming machines. This object is solved by a hydraulic drive device according to claim 1. It is therefore provided according to the invention that the working pressure chamber remote from the region of the piston defines a low pressure chamber which is pressurized during operation of the device by a low pressure supply for hydraulic fluid such that the piston is moved back against the working direction when the control means connects the working pressure chamber with the return chamber ,
[0006] Dadurch, dass die Rückbewegung des Kolbens durch Hydraulikflüssigkeit von einer Niederdruckversorgung bewirkt wird, wird bei einem Arbeitszyklus aus Vorfahren und Rückfahren des Kolbens der Energiebedarf der Vorrichtung erheblich verringert. Insbesondere im Einsatz in Stanz-, Präge-, Nibbel-, Biege- oder Umformmaschinen mit prinzipbedingt hohen Wiederholungszahlen der Arbeitszyklen ergibt sich eine große Energieersparnis. Bei den bisher aus dem Stand der Technik bekannten hydraulischen Antriebsvorrichtungen ist dagegen auch die Rückbewegung des Kolbens mit einem Volumenstrom von Hydraulikflüssigkeit aus einer Hochdruckversorgung verbunden, was einen erheblichen energetischen Verlust mit sich bringt.Characterized in that the return movement of the piston is caused by hydraulic fluid from a low pressure supply, the energy requirement of the device is significantly reduced in a working cycle of ancestors and return of the piston. In particular, when used in stamping, embossing, nibbling, bending or forming machines with inherently high repetition rates of the working cycles results in a large energy savings. In contrast, in the hydraulic drive devices known hitherto from the prior art, the return movement of the piston is connected to a volume flow of hydraulic fluid from a high-pressure supply, which entails a considerable loss of energy.
[0007] Der Kolben begrenzt vorteilhafterweise nicht nur den Arbeitsdruckraum und den Rücklaufraum, sondern auch einen Hochdruckraum und einen Niederdruckraum. Eine Druckbeaufschlagung des Arbeitsdruckraums mit Hydraulikflüssigkeit bewirkt dabei eine Kraft auf den Kolben in Arbeitsrichtung, während eine Druckbeaufschlagung des Niederdruckraums eine Kraft auf den Kolben entgegen der Arbeitsrichtung bewirkt. Der Rücklaufraum ist insbesondere über einen Tankanschluss mit einem Tank verbunden und dient zum Abführen der Hydraulikflüssigkeit aus dem Arbeitsdruckraum. Der Hochdruckraum ist insbesondere über einen Hochdruckanschluss mit der Hochdruckversorgung verbunden und dient zur Versorgung des Arbeitsdruckraums mit Hydraulikflüssigkeit. Davon getrennt ist der Niederdruckraum insbesondere über einen Niederdruckanschluss mit der Niederdruckversorgung verbunden. Der Hochdruckraum und der Niederdruckraum sind dabei insbesondere so ausgebildet, dass bei Druckbeaufschlagung keine auf den Arbeitskolben in oder gegen die Arbeitsrichtung resultierende KräfteThe piston advantageously not only limits the working pressure chamber and the return chamber, but also a high-pressure chamber and a low-pressure chamber. A pressurization of the working pressure chamber with hydraulic fluid causes a force on the piston in the working direction, while pressurization of the low-pressure chamber causes a force on the piston against the working direction. The return chamber is connected in particular via a tank connection with a tank and serves to discharge the hydraulic fluid from the working pressure chamber. The high-pressure chamber is connected in particular via a high-pressure connection to the high-pressure supply and serves to supply the working pressure chamber with hydraulic fluid. Separated from this, the low-pressure space is connected in particular via a low-pressure connection to the low-pressure supply. The high pressure chamber and the low pressure chamber are in particular so designed that when pressurized no resulting forces on the piston in or against the working direction
[0008] Eine Weiterbildung der Erfindung sieht vor, dass der Niederdruckraum unabhängig vom Steuerzustand des Steuermittels von der Hochdruckversorgung getrennt ist. Der Hochdruckversorgung wird damit nur während des Arbeitsschritts (d.h. während des Vorfahrens) Hydraulikflüssigkeit entnommen, bei dem durch Befüllen des Arbeitsdruckraums mit Hydraulikflüssigkeit der Kolben in Arbeitsrichtung bewegt wird. Beim Rückbewegen des Kolbens fließt keine Hydraulikflüssigkeit von der Hochdruckversorgung.A further development of the invention provides that the low-pressure chamber is separated from the high-pressure supply independently of the control state of the control means. The high-pressure supply is thus removed only during the working step (i.e., during the pre-driving) hydraulic fluid in which the piston is moved in the working direction by filling the working pressure chamber with hydraulic fluid. When the piston is moved back, no hydraulic fluid flows from the high pressure supply.
[0009] Als bevorzugte Ausgestaltung der Erfindung sind Einstellmittel vorgesehen, mittels welchen der Druck der Hochdruckversorgung abhängig vom Verfahrweg des Kolbens und/oder der Arbeitslast des Kolbens einstellbar ist. Damit wird eine weitere Energieersparnis ermöglicht, da die volle Kraftwirkung des Kolbens oftmals nur für einen Bruchteil der gesamten Kolbenbewegung benötigt wird. Es wird folglich nicht nur beim Rückfahren des Kolbens, wie vorstehend beschrieben, Energie eingespart, sondern es kann auch während des Vorfahrens des Kolbens der Energiebedarf verringert werden.As a preferred embodiment of the invention adjusting means are provided, by means of which the pressure of the high-pressure supply is adjustable depending on the travel of the piston and / or the workload of the piston. Thus, a further energy savings is possible because the full force of the piston is often required only for a fraction of the total piston movement. As a result, energy is not only saved during the return movement of the piston, as described above, but the energy requirement can also be reduced during the advancement of the piston.
[0010] Vorteilhafterweise sind die Einstellmittel derart ausgebildet, dass derAdvantageously, the adjusting means are designed such that the
Druck der Hochdruckversorgung zum Bewegen des Kolbens aus seiner rückgefahrenen Endlage in Arbeitsrichtung bis zur oder bis kurz vor der Aufnahme einer Arbeitslast einen Wert p1 und anschließend, insbesondere während der Arbeitslast, einen Wert p2 aufweist. Dabei ist p1 kleiner als p2.Pressure of the high-pressure supply for moving the piston from its retracted end position in the working direction until or until shortly before receiving a workload a value p1 and then, in particular during the workload, a value p2. Here p1 is smaller than p2.
[0011] Ferner sind die Einstellmittel vorteilhafterweise derart ausgebildet, dass bei einem weiteren Bewegen des Kolbens in Arbeitsrichtung nach der Überwindung der Arbeitslast der Druck der Hochdruckversorgung einen Wert p3 aufweist, wobei p3 kleiner als p2 und/oder p3 gleich p1 ist.Further, the adjusting means are advantageously designed such that upon further movement of the piston in the working direction after overcoming the workload, the pressure of the high pressure supply has a value p3, p3 is less than p2 and / or p3 is equal to p1.
[0012] Damit wird erreicht, dass ein erhöhter Leistungsbedarf derThis ensures that an increased power requirement of
Hochdruckquelle nur im Bereich der Arbeitslast auftritt, beispielsweise während des Umformens eines Werkstücks durch die Kolbenbewegung. Das Vorfahren des Kolbens bis zum Einsetzten der Arbeitslast erfolgt unter geringerem Energieaufwand.High pressure source occurs only in the range of workload, for example, during the forming of a workpiece by the piston movement. The ancestor of the piston to the onset of the workload is done with less energy.
[0013] Als vorteilhafte Weiterbildung ist ein Wegmesssystem zur Bestimmung des Verfahrwegs (d.h. der Position) des Kolbens und/oder ein Lastmesssystem zur Bestimmung der Arbeitslast des Kolbens vorgesehen. Im Zusammenwirken mit den Einstellmitteln für den Druck der Hochdruckversorgung ermöglichen diese Messsysteme eine optimierte Hochdruckzuschaltung zur weiteren Energieersparnis.As an advantageous development, a displacement measuring system for determining the travel path (i.e., the position) of the piston and / or a load measuring system for determining the working load of the piston is provided. In conjunction with the adjustment means for the pressure of the high-pressure supply, these measuring systems enable optimized high-pressure connection for further energy savings.
[0014] Als weitere Ausgestaltung der Erfindung ist vorgesehen, dass dasAs a further embodiment of the invention, it is provided that the
Steuermittel in dem Bereich, in dem es im Kolben geführt ist, längs der Arbeitsrichtung einen Druckraum begrenzt, der mit dem Niederdruckraum druckverbunden ist.Control means in the region in which it is guided in the piston, limited along the working direction of a pressure chamber, which is pressure-connected to the low-pressure space.
[0015] Eine bevorzugte Ausführungsform der Erfindung ergibt sich daraus, dass das Steuermittel als ein längs der Arbeitsachse geführter Steuerschieber ausgeführt ist, welcher wenigstens abschnittsweise im Inneren des Kolbens geführt wird, und welcher Steuerkanten aufweist, die zur Zusammenwirkung mit weiteren Steuerkanten am Kolben ausgebildet sind, um den Durchfluss von Hydraulikflüssigkeit in den oder aus dem Arbeitsdruckraum zu steuern. Wenn der Steuerschieber wie vorhergehend beschrieben in dem Bereich, in dem er im Kolben geführt ist, längs der Arbeitsrichtung einen Druckraum begrenzt, der mit dem Niederdruckraum druckverbunden ist, erfährt der Steuerschieber ununterbrochen eine Kraft gegen die Arbeitsrichtung. Zur Betätigung muss der Steuerschieber daher lediglich in Arbeitsrichtung geschoben, nicht entgegengesetzt gezogen werden. Alternativ ist auch denkbar, ein um seine Längsachse rotierbares Steuermittel zu verwenden.A preferred embodiment of the invention results from the fact that the control means is designed as a guided along the working axis spool, which is guided at least partially inside the piston, and which has control edges, which are designed to cooperate with further control edges on the piston to control the flow of hydraulic fluid into or out of the working pressure space. As described above, when the spool in the region where it is guided in the piston defines a pressure space along the working direction that is pressure-connected to the low-pressure space, the spool continuously receives a force against the working direction. For actuation of the spool must therefore only pushed in the direction of work, not pulled opposite. Alternatively, it is also conceivable to use a control means rotatable about its longitudinal axis.
[0016] Der Steuerschieber kann dabei einstückig oder auch mehrteilig ausgebildet sein, wobei einzelne Teile des Steuerschiebers insbesondere über Gelenke miteinander verbunden sein können. Hierdurch können insbesondere Fluchtungsfehler ausgeglichen werden.The spool may be formed integrally or in several parts, with individual parts of the spool can be connected to each other in particular via joints. As a result, in particular alignment errors can be compensated.
[0017] Der Steuerschieber kann außerdem einerseits in dem an den Niederdruckraum angrenzenden Bereich des Kolbens in einer zylindrischen Führungsöffnung und andererseits im Zylindergehäuse in einer weiteren zylindrischen Führungsöffnung geführt werden, wobei die Führungsöffnungen den gleichen Durchmesser aufweisen.The spool can also on the one hand in the adjacent to the low-pressure chamber region of the piston in a cylindrical guide opening and on the other hand in the cylinder housing in a further cylindrical guide opening are guided, wherein the guide openings have the same diameter.
[0018] Als Weiterbildung der Erfindung ist eine Koppelstange zur Betätigung des Steuerschiebers derart vorgesehen, dass der Steuerschieber mittels der Koppelstange in Arbeitsrichtung des Kolbens geschoben werden kann. Wenn der Steuerschieber wie oben beschrieben einen Druckraum im Kolben begrenzt, der mit dem Niederdruckraum druckverbunden ist, wirkt damit auf den Steuerschieber ununterbrochen eine Kraft entgegen der Arbeitsrichtung. Die Koppelstange muss daher zur Betätigung des Steuerschiebers diesen lediglich in Arbeitsrichtung schieben, den Steuerschieber aber nicht ziehen. Es ist damit nicht notwendig, dass Steuerstange und Steuerschieber fest miteinander verbunden werden. Insbesondere kann die Koppelstange nur lose am Steuerschieber anliegen.As a development of the invention, a coupling rod for actuating the spool is provided such that the spool can be pushed by means of the coupling rod in the direction of the piston. If the spool as described above defines a pressure chamber in the piston, which is pressure-connected to the low-pressure chamber, thus acting on the spool uninterrupted a force counter to the working direction. The coupling rod therefore has to push this to actuate the spool this only in the working direction, but not pull the spool. It is therefore not necessary that control rod and spool are firmly connected. In particular, the coupling rod can rest only loosely on the spool.
[0019] Vorteilhafterweise wird die Koppelstange mit einem elektromechanischen Wandler verbunden. Insbesondere kann vorgesehen sein, dass der elektromechanische Wandler als Linear-Direktmotor ausgeführt ist und dessen längs der Arbeitsachse bewegbare Läufer mit der Koppelstange fest verbunden ist.Advantageously, the coupling rod is connected to an electromechanical transducer. In particular, it can be provided that the electromechanical transducer is designed as a linear direct motor and its longitudinal axis movable along the working rotor is firmly connected to the coupling rod.
[0020] Zur Lösung der eingangs gestellten Aufgabe wird außerdem ein Verfahren mit den Merkmalen des Anspruchs 12 bereitgestellt. Bei dem Verfahren zum Betrieb einer hydraulischen Arbeitsvorrichtung mit einem in einem Zylinderraum verschiebbar geführten Kolben, welcher einen Arbeitsdruckraum begrenzt, wird der Arbeitsdruckraum zum Bewegen des Kolbens in Arbeitsrichtung mit Hydraulikflüssigkeit mit einem Hochdruck PH beaufschlagt. Erfindungsgemäß wird zum Rückbewegen des Kolbens entgegen der Arbeitsrichtung ein Niederdruckraum, der durch einen dem Arbeitsdruckraum abgewandten Bereich des Kolbens begrenzt ist, mit einem Niederdruck PN beaufschlagt. Dabei gilt PN <= PH. Zur Durchführung des Verfahrens findet insbesondere eine erfindungsgemäße hydraulische Antriebsvorrichtung Verwendung. Damit wird erreicht, dass die Rückbewegung des Kolbens entgegen der Arbeitsrichtung in energiesparender Weise durch Hydraulikflüssigkeit mit niederem Druck herbeigeführt wird. Hydraulikflüssigkeit mit hohem Druck wird nur zur Bewegung des Kolbens in Arbeitsrichtung benötigt.To achieve the object stated at the outset, a method with the features of claim 12 is also provided. In the method for operating a hydraulic working device with a displaceably guided in a cylinder chamber piston which limits a working pressure chamber, the working pressure chamber for moving the piston in the working direction with hydraulic fluid with a high pressure PH is applied. According to the invention, a low-pressure space, which is delimited by a region of the piston facing away from the working pressure chamber, is acted upon by a low-pressure PN to move the piston back against the working direction. Where PN <= PH. For carrying out the method, in particular a hydraulic drive device according to the invention is used. This ensures that the return movement of the piston counter to the working direction in an energy-saving manner by hydraulic fluid at low pressure is brought about. High pressure hydraulic fluid is only needed to move the piston in the direction of operation.
[0021] Das Verfahren kann dadurch weiter ausgestaltet sein, dass der Druck der den Arbeitsdruckraum druckbeaufschlagenden Hydraulikflüssigkeit abhängig vom Verfahrweg des Kolbens und/oder der Arbeitslast des Kolbens eingestellt wird.The method can be further configured that the pressure of the working pressure chamber pressurizing hydraulic fluid is adjusted depending on the travel of the piston and / or the workload of the piston.
[0022] Als weitere Ausgestaltung wird der Niederdruckraum ununterbrochen mit Niederdruck beaufschlagt.As a further embodiment of the low-pressure chamber is continuously applied with low pressure.
[0023] Besonders bevorzugt ist, wenn der Hochdruck der den Arbeitsdruckraum druckbeaufschlagenden Hydraulikflüssigkeit zum Bewegen des Kolbens aus seiner rückgefahrenen Endlage in Arbeitsrichtung bis zur oder bis kurz vor der Aufnahme einer Arbeitslast einen Wert p1 und anschließend, insbesondere während der Arbeitslast, einen Wert p2 aufweist, wobei p1 kleiner als p2 ist. Für den Fall, dass ein weiteres Bewegen des Kolbens nach der Überwindung der Arbeitslast in Arbeitsrichtung vorgesehen ist, weist der Hochdruck einen Wert p3 auf, wobei p3 kleiner p2 und/oder p3 gleich p1 ist.It is particularly preferred if the high pressure of the working pressure chamber pressurizing hydraulic fluid for moving the piston from its retracted end position in the working direction until or shortly before receiving a workload a value p1 and then, in particular during the workload, a value p2 where p1 is less than p2. In the event that a further movement of the piston is provided after overcoming the working load in the working direction, the high pressure has a value p3, where p3 is less than p2 and / or p3 is equal to p1.
[0024] Weitere Einzelheiten und vorteilhafte Ausgestaltungen der Erfindung sind der folgenden Beschreibung zu entnehmen, anhand derer die in den Figuren dargestellte Ausführungsform der Erfindung näher beschrieben und erläutert wird.Further details and advantageous embodiments of the invention will become apparent from the following description, with reference to which the embodiment of the invention shown in the figures is described and explained in more detail.
[0025] Es zeigen:In the drawings:
[0026] Figur 1 einen Längsschnitt durch eine erfindungsgemäße hydraulische Antriebsvorrichtung in Ruhestellung,1 shows a longitudinal section through a hydraulic drive device according to the invention in the rest position,
[0027] Figur 2 einen Teil der Antriebsvorrichtung gemäß Figur 1 im Zustand zum Ausfahren des Kolbens als Längsschnitt,FIG. 2 shows a part of the drive device according to FIG. 1 in the state for extending the piston as a longitudinal section;
[0028] Figur 3 einen Teil der Antriebsvorrichtung gemäß Figur 1 im Zustand zum Rückfahren des Kolbens als Längsschnitt,3 shows a part of the drive device according to FIG. 1 in the state for returning the piston as a longitudinal section, FIG.
[0029] Figur 4 den Zeitverlauf des Verfahrweges des Kolbens und des eingestellten Druckes der Hochdruckversorgung.Figure 4 shows the time course of the travel of the piston and the set pressure of the high pressure supply.
[0030] Die in den Figuren 1 - 3 dargestellten hydraulische Arbeitsvorrichtung weist einen Zylinder 3 und einen Kolben 5 auf. Der Kolben 5 ist in einem Zylinderraum 8 längs einer Arbeitsachse 10 verschiebbar und dichtend geführt. Der Kolben 5 ist einstückig mit einer Kolbenstange 6 verbunden, die den Zylinder 3 in einer Arbeitsrichtung 11 überragt. Die Kolbenstange 6 kann beispielsweise mit einem Stanzwerkzeug (nicht dargestellt) zum Umformen eines Werkstücks (nicht dargestellt) verbunden werden. Der Kolben 5 begrenzt einen Arbeitsdruckraum 13, einen Rücklaufraum 15, einen Hochdruckraum 17 und einen Niederdruckraum 19, welche zum Betrieb der Vorrichtung in der weiter unten beschriebenen Weise mit Hydraulikflüssigkeit befüllt werden. Eine Druckbeaufschlagung des Arbeitsdruckraums 13 mit Hydraulikflüssigkeit bewirkt dabei eine Kraft auf den Kolben 5 in Arbeitsrichtung 11 , während eine Druckbeaufschlagung des Niederdruckraums 19 eine Kraft auf den Kolben 5 entgegen der Arbeitsrichtung 11 bewirkt. Der Rücklaufraum 15 ist über einen Tankanschluss 16 mit einem Tank 22 verbunden und dient zum Abführen der Hydraulikflüssigkeit. Der Hochdruckraum 17 ist über einen Hochdruckanschluss 18 mit einer Hochdruckversorgung 24 für Hydraulikflüssigkeit verbunden und dient zur Versorgung des Arbeitsdruckraums 13 mit Hydraulikflüssigkeit. Davon getrennt ist der Niederdruckraum 19 über einen Niederdruckanschluss 20 mit einer Niederdruckversorgung 26 für Hydraulikflüssigkeit verbunden.The hydraulic working device illustrated in FIGS. 1-3 has a cylinder 3 and a piston 5. The piston 5 is displaceable and sealing in a cylinder chamber 8 along a working axis 10 guided. The piston 5 is integrally connected to a piston rod 6, which projects beyond the cylinder 3 in a working direction 11. For example, the piston rod 6 may be connected to a punching tool (not shown) for forming a workpiece (not shown). The piston 5 defines a working pressure chamber 13, a return chamber 15, a high pressure chamber 17 and a low pressure chamber 19, which are filled with hydraulic fluid for operating the device in the manner described below. Pressurization of the working pressure chamber 13 with hydraulic fluid causes a force on the piston 5 in the working direction 11, while pressurization of the low-pressure chamber 19 causes a force on the piston 5 against the working direction 11. The return chamber 15 is connected via a tank connection 16 with a tank 22 and serves to discharge the hydraulic fluid. The high pressure chamber 17 is connected via a high pressure port 18 to a high pressure supply 24 for hydraulic fluid and serves to supply the working pressure chamber 13 with hydraulic fluid. Separated from this, the low-pressure space 19 is connected via a low-pressure connection 20 to a low-pressure supply 26 for hydraulic fluid.
[0031] Der Kolben 5 hat eine koaxiale zylindrische Bohrung 28, in der ein Steuermittel 29 in Form eines Steuerschiebers 30 entlang der Arbeitsachse 10 längs verschiebbar und dichtend geführt ist. Die axialen Endbereiche 32 und 34 des Steuerschiebers 30 sind kolbenartig ausgebildet. Der kolbenseitige Endbereich 32 wird dabei in einer zylindrischen Führungsbohrung 36 im Kolben 5 dichtend geführt und begrenzt im Kolben 5 einen Druckraum 38, welcher mit dem Niederdruckraum 19 druckverbunden ist. Der dem Kolben 5 abgewandte Endbereich 34 des Steuerschiebers 30 ist in einer zylindrischen Führungsbohrung 40 im Zylinder 3 dichtend geführt. Die Durchmesser der Führungsbohrungen 36 und 40 sind dabei gleich groß.The piston 5 has a coaxial cylindrical bore 28 in which a control means 29 in the form of a spool 30 along the working axis 10 is guided longitudinally displaceable and sealing. The axial end portions 32 and 34 of the spool 30 are formed like a piston. The piston-side end portion 32 is sealingly guided in a cylindrical guide bore 36 in the piston 5 and limited in the piston 5 a pressure chamber 38 which is pressure-connected to the low-pressure chamber 19. The piston 5 facing away from the end portion 34 of the spool 30 is sealingly guided in a cylindrical guide bore 40 in the cylinder 3. The diameters of the guide bores 36 and 40 are the same size.
[0032] Der Steuerschieber 30 weist Durchgangsfenster 48 mit Steuerkanten 42 und 43 auf. Diese sind zur Zusammenwirkung mit Steuerkanten 45 und 46 am Kolben ausgebildet, um eine hydraulische Folgeregelung für Kolben 5 und Steuerschieber 30 bereitzustellen. Der Rϋcklaufraum 15 und der Hochdruckraum 17 weisen dazu Durchflussöffnungen 41 und 44 auf, welche den Rücklaufraum 15 und den Hochdruckraum mit der axialen Bohrung 28 für den Steuerschieber 30 verbinden. Die kolbenseitigen Steuerkanten 45 stehen dabei mit der Durchflussöffnung 41 und damit mit dem Rücklaufraum 15 in Verbindung, die kolbenseitigen Steuerkanten 46 mit der Durchflussöffnung 44 und damit mit dem Hochdruckraum 17. Die Steuerkanten 42 und 43 am Steuerschieber 30 haben denselben oder einen geringfügig kleineren Abstand voneinander, als die zugeordneten Steuerkanten 45 und 46. Durch Verschieben des Steuerschiebers 30 längs der Arbeitsachse 10 kann folglich der Arbeitsdruckraum 13 entweder mit dem Rücklaufraum 15, oder mit dem Hochdruckraum 17 druckverbunden werden. Der Niederdruckraum 19 weist unabhängig von der Stellung des Steuerschiebers 30 keine Druckverbindung zum Hochdruckraum 17 oder zum Rücklaufraum 15 auf.The spool 30 has through windows 48 with control edges 42 and 43. These are designed to cooperate with control edges 45 and 46 on the piston to a hydraulic follow-up control for piston. 5 and spool 30 to provide. The return chamber 15 and the high-pressure chamber 17 have flow openings 41 and 44, which connect the return chamber 15 and the high-pressure chamber with the axial bore 28 for the spool 30. The piston-side control edges 45 are in communication with the flow opening 41 and thus with the return chamber 15, the piston-side control edges 46 with the flow opening 44 and thus with the high pressure chamber 17. The control edges 42 and 43 on the spool 30 have the same or a slightly smaller distance from each other By shifting the spool 30 along the working axis 10, consequently, the working pressure space 13 can be pressure-connected either to the return space 15 or to the high-pressure space 17. The low-pressure chamber 19, regardless of the position of the spool 30 has no pressure connection to the high-pressure chamber 17 or to the return chamber 15.
[0033] Zur Betätigung des Steuerschiebers 30 ist eine Koppelstange 50 vorgesehen, mittels welcher der Steuerschieber 30 in Arbeitsrichtung 11 geschoben werden kann. Die Koppelstange 50 liegt dabei nur lose am kolbenartigen Endbereich 34 des Steuerschiebers 30 an. Die Koppelstange 50 ist andererseits fest mit dem Läufer 52 eines elektromechanischen Wandlers 54, der insbesondere als Linear- Direktmotor ausgeführt ist, verbunden.For actuating the spool 30, a coupling rod 50 is provided, by means of which the spool 30 can be pushed in the direction of work 11. The coupling rod 50 is only loosely on the piston-like end portion 34 of the spool 30 at. On the other hand, the coupling rod 50 is firmly connected to the rotor 52 of an electromechanical converter 54, which is designed in particular as a linear direct motor.
[0034] Zur Einstellung des Drucks der Hochdruckversorgung 24 sind Einstellmittel 60 vorgesehen. Diese stellen den Druck der Hochdruckversorgung 24 abhängig vom Verfahrweg, d.h. der Position des Kolbens 5 entlang der Arbeitsrichtung 11 ein. Die Position des Kolbens 5 längs der Arbeitsachse 10 wird über ein Wegmesssystem 62 ermittelt. Ferner kann vorgesehen sein, dass die Einstellmittel 60 den Druck der Hochdruckversorgung 24 in Abhängigkeit der Arbeitslast des Kolbens 5 einstellen, welche mittels eines Lastmesssystems (nicht dargestellt) bestimmt werden.To adjust the pressure of the high pressure supply 24 adjustment means 60 are provided. These set the pressure of the high pressure supply 24 dependent on the travel, i. the position of the piston 5 along the working direction 11 a. The position of the piston 5 along the working axis 10 is determined via a displacement measuring system 62. Furthermore, it can be provided that the adjusting means 60 adjust the pressure of the high pressure supply 24 as a function of the working load of the piston 5, which are determined by means of a load measuring system (not shown).
[0035] Im Betrieb arbeitet die hydraulische Antriebsvorrichtung 1 in der nachfolgend beschriebenen Weise. In der in Figur 1 dargestellten Ruhelage wird der Steuerschieber 30 durch die Koppelstange 50 in Ruhestellung gehalten. Dabei wird die durch den Niederdruck im Druckraum 38 auf den Steuerschieber 30 wirkende Kraft entgegen der Arbeitsrichtung 11 durch die Steuerstange 50 kompensiert. Es herrscht außerdem Kräftegleichgewicht zwischen der in Arbeitsrichtung 11 wirkenden Kraft auf den Kolben 5 durch die im Arbeitsdruckraum 13 befindliche Hydraulikflüssigkeit und die der Arbeitsrichtung 11 entgegenwirkende Kraft auf den Kolben 5 durch die im Niederdruckraum 19 befindliche Hydraulikflüssigkeit. Ein Durchfluss von Hydraulikflüssigkeit vom Hochdruckraum 17 in den Arbeitsdruckraum 13 oder vom Arbeitsdruckraum 13 in den Rücklaufraum 15 wird verhindert, da die Durchflussöffnungen 41 und 44 dichtend vom Steuerschieber 30 bedeckt sind.In operation, the hydraulic drive device 1 operates in the manner described below. In the illustrated in Figure 1 Rest position, the spool 30 is held by the coupling rod 50 in the rest position. In this case, the force acting on the spool 30 by the low pressure in the pressure chamber 38 is counteracted counter to the working direction 11 by the control rod 50. There is also force equilibrium between the force acting in the working direction 11 on the piston 5 through the hydraulic fluid in the working pressure chamber 13 and the working direction 11 counteracting force on the piston 5 through the low pressure chamber 19 located hydraulic fluid. A flow of hydraulic fluid from the high pressure chamber 17 in the working pressure chamber 13 or the working pressure chamber 13 in the return chamber 15 is prevented, since the flow openings 41 and 44 are sealingly covered by the spool 30.
[0036] Wird die Koppelstange 50 durch den Linear-Direktmotor 54 in Arbeitsrichtung bewegt, so schiebt die Koppelstange 50 den Steuerschieber 30 ebenfalls in Arbeitsrichtung. Wie in Figur 2 dargestellt, öffnet sich dadurch ein Spalt zwischen den Steuerkanten 43 am Steuerschieber 30 und den Steuerkanten 46 am Kolben 5. Dadurch wird der Hochdruckraum 17 mit dem Arbeitsdruckraum 13 druckverbunden und Hydraulikflüssigkeit strömt von der Hochdruckversorgung 24 über den Hochdruckraum 17 durch die Durchgangsfenster 48 in den Arbeitsdruckraum 13. Dadurch wirkt eine Kraft in Arbeitsrichtung 11 auf den Kolben 5 und der Kolben 5 wird in Arbeitsrichtung 11 bewegt. Der Kolben 5 folgt so lange der Bewegung des Steuerschiebers 30, bis die Steuerkanten 43 und 46 wieder wie in Figur 1 dargestellt schließen, so dass ein Durchfluss von Hydraulikflüssigkeit vom Hochdruckraum 17 in den Arbeitsdruckraum 13 oder vom Arbeitsdruckraum 13 in den Rücklaufraum 15 unterbunden wird. Es stellt sich daraufhin wieder eine Ruhelage ähnlich der in Figur 1 dargestellten Situation ein.If the coupling rod 50 is moved by the linear direct motor 54 in the working direction, the coupling rod 50 pushes the spool 30 also in the working direction. As shown in Figure 2, thereby opening a gap between the control edges 43 on the spool 30 and the control edges 46 on the piston 5. As a result, the high-pressure chamber 17 is pressure-connected to the working pressure chamber 13 and hydraulic fluid flows from the high-pressure supply 24 via the high-pressure chamber 17 through the passage window 48 in the working pressure chamber 13. As a result, a force in the working direction 11 acts on the piston 5 and the piston 5 is moved in the working direction 11. The piston 5 follows the movement of the spool 30 until the control edges 43 and 46 close again as shown in Figure 1, so that a flow of hydraulic fluid from the high-pressure chamber 17 is prevented in the working pressure chamber 13 or the working pressure chamber 13 in the return chamber 15. As a result, a rest position similar to the situation illustrated in FIG. 1 occurs again.
[0037] Der im Wesentlichen als Ringraum ausgebildete Hochdruckraum 17 erstreckt sich soweit in Axialrichtung, dass der Hochdruckanschluss 18 über den gesamten Hub mit der Durchflussöffnung 44 in Verbindung steht. Im Betrieb wir zwar auch bei vom Steuerschieber 30 verschlossener Durchflussöffnung 44 der Hochdruckraum 17 mit Hochdruck beaufschlagt; eine daraus resultierende Kraft, die den Kolben 5 in eine Richtung bewegt, resultiert hieraus allerdings nicht. Anstelle des Hochdruckraums 17 könnte auch eine Schlauchverbindung zwischen dem Hochdruckanschluss 18 und der Durchflussöffnung 44 vorgesehen sein.The high-pressure chamber 17, which is designed essentially as an annular space, extends so far in the axial direction that the high-pressure port 18 communicates with the flow opening 44 over the entire stroke. In operation, we also closed off by the spool 30 Flow opening 44 of the high-pressure chamber 17 is subjected to high pressure; however, a resultant force that moves the piston 5 in one direction does not result. Instead of the high-pressure chamber 17, a hose connection between the high-pressure connection 18 and the flow-through opening 44 could also be provided.
[0038] Entsprechendes gilt für den ebenfalls als Ringraum ausgebildeten Rücklaufraum 15; er verbindet die Durchflussöffnung 41 mit dem Tankanschluss 16, ohne dass eine auf den Kolben 5 resultierende Kraft wirkt. Auch hier könnte eine Schlauchverbindung zwischen dem Tankanschluss 16 und der Durchflussöffnung 41 vorgesehen sein.The same applies to the also formed as an annular space return chamber 15; it connects the flow opening 41 with the tank connection 16, without any force acting on the piston 5 acting. Again, a hose connection between the tank port 16 and the flow opening 41 may be provided.
[0039] Zum Rückbewegen des Kolbens entgegen der Arbeitsrichtung 11 wird die Koppelstange 50 durch den Linear-Direktmotor 54 entgegen der Arbeitsrichtung vom Endbereich 34 des Steuerschiebers 30 weg bewegt. Durch den im Druckraum 38 herrschenden Niederdruck wird der Steuerschieber 30 entgegen der Arbeitsrichtung 11 bewegt. Wie in Figur 3 dargestellt, öffnet sich dadurch ein Spalt zwischen den Steuerkanten 42 am Steuerschiebers 30 und den Steuerkanten 45 am Kolben 5, so dass der Arbeitsdruckraum 13 mit dem Rücklaufraum 15 druckverbunden wird. Durch den im Niederdruckraum 19 herrschenden niederen Druck wirkt eine Kraft entgegen der Arbeitsrichtung 11 auf den Kolben 5. Der Kolben 5 kann sich nun entgegen der Arbeitsrichtung 11 bewegen, wobei die sich im Arbeitsdruckraum 13 befindliche Hydraulikflüssigkeit durch die Durchgangsfenster 48 in den Rücklaufraum 15 und von dort in den Tank 22 verdrängt wird. Der Kolben 5 und der Steuerschieber 30 bewegen sich so lange entgegen der Arbeitsrichtung 11 , bis eine weitere Bewegung des Steuerschiebers 30 durch ein Anstoßen des Endbereichs 34 des Steuerschiebers 30 an die Koppelstange 50 verhindert wird. Dann verschiebt sich der Steuerschieber wieder in eine Lage, in welcher der Spalt zwischen den Steuerkanten 42 und 45 verschlossen ist. Es stellt sich dann wieder eine Ruhelage ähnlich der Figur 1 dargestellte Ruhelage ein.To move back the piston against the working direction 11, the coupling rod 50 is moved by the linear direct motor 54 against the working direction of the end portion 34 of the spool 30 away. Due to the pressure prevailing in the pressure chamber 38 low pressure of the spool 30 is moved counter to the working direction 11. As shown in Figure 3, thereby opens a gap between the control edges 42 on the spool 30 and the control edges 45 on the piston 5, so that the working pressure chamber 13 is pressure-connected to the return chamber 15. Due to the low pressure prevailing in the low pressure chamber 19, a force counteracts the working direction 11 on the piston 5. The piston 5 can now move counter to the working direction 11, wherein the hydraulic fluid located in the working pressure chamber 13 through the passage window 48 in the return chamber 15 and there is displaced into the tank 22. The piston 5 and the spool 30 move so long against the working direction 11 until further movement of the spool 30 is prevented by abutment of the end portion 34 of the spool 30 to the coupling rod 50. Then, the spool shifts back into a position in which the gap between the control edges 42 and 45 is closed. It turns then again a rest position similar to the figure 1 shown rest position.
[0040] Im typischen Einsatz der beschriebenen hydraulischen Antriebsvorrichtung in einer Stanzmaschine für Metallwerkstücke wird die volle Arbeitskraft des Kolbens 5 in Arbeitsrichtung 11 nicht während des gesamten Arbeitszyklus aus Vor- und Rϋckfahren des Kolbens 5 benötigt. Vielmehr wird die volle Arbeitskraft lediglich beim Auftreffen eines mit der Kolbenstange 6 verbundenen Stanzwerkzeugs (nicht dargestellt) auf ein Werkstück (nicht dargestellt) und während des Durchdringens des Werkstücks benötigt. Im beschriebenen Ausführungsbeispiel ist daher vorgesehen, dass die Einstellmittel 60 den Druck der Hochdruckversorgung 24 abhängig vom Verfahrweg, d.h. von der Position des Kolbens 5 einstellen. In Figur 4 ist der Zeitverlauf der Position des Kolbens 5 zusammen mit dem Zeitverlauf des durch die Einstellmittel 60 eingestellten Drucks der Hochdruckversorgung 24 dargestellt. Ausgehend von der rückgefahrenen Endlage POSO des Kolbens 5 wird der Kolben 5 in Arbeitsrichtung 11 bis zu der Position POS1 bewegt, in welcher das mit der Kolbenstange verbundene Stanzwerkzeug auf das zu verformende Werkstück auftrifft. Für diesen Verfahrweg wird der Druck der Hochdruckversorgung 24 auf einen niedrigen Wert p1 eingestellt, der insbesondere gleich dem der Niederdruckversorgung 26 gewählt sein kann. Der Verfahrweg wird dabei durch das Wegmesssystem 62 erfasst und mit einem voreingestelltem Wert verglichen, welcher beispielsweise der Distanz des Stanzwerkzeuges in rückgefahrener Endlage des Kolbens 5 zum Werkstück entspricht. Hat sich der Kolben über die genannte Distanz bewegt, so triff das Stanzwerkzeug auf das zu verformende Werkstück. Dies geschieht an der in Figur 4 mit POS1 bezeichneten Position des Kolbens. Dann erhöhen die Einstellmittel 60 den Druck der Hochdruckversorgung 24 auf einen Wert p2, der deutlich höher als p1 ist und typischerweise dem Maximaldruck der Hochdruckversorgung 24 entspricht. Dieser Hochdruck wird für die weitere Bewegung des Kolbens 5 in Arbeitsrichtung 11 so lange aufrechterhalten, bis das an der Kolbenstange 6 angebrachte Stanzwerkzeug das Werkstück durchdrungen hat (Position POS2 des Kolbens 5 in Figur 4). Damit lässt die Arbeitslast auf den Kolben 5 nach. Falls ein weiteres Bewegen des Kolbens 5 in Arbeitsrichtung 11 bis zur Position POS3 vorgesehen ist, verringern die Einstellmittel 60 den Druck der Hochdruckversorgung 24 auf einen Wert p3, der kleiner als der Druck p2 und insbesondere gleich dem Druck der Niederdruckversorgung 26 ist. [0042] Während der Rückbewegung des Kolbens 5 entgegen der Arbeitsrichtung 11 blockiert der Steuerschieber 30 einen weiteren Durchfluss von Hydraulikflüssigkeit von der Hochdruckversorgung 24 in den Arbeitsdruckraum 13. Ein energieaufwändiger Volumenstrom von Hydraulikflüssigkeit von der Hochdruckversorgung 24 wird daher unterbunden. Die Rückbewegung wird lediglich durch einen Volumenstrom von Hydraulikflüssigkeit von der Niederdruckversorgung 26 bewirkt.In typical use of the described hydraulic drive device in a punching machine for metal workpieces, the full working force of the piston 5 in the working direction 11 is not during the entire working cycle from forward and backward travel of the piston 5 is required. Rather, the full working force is only required when striking a piston rod 6 connected to the punching tool (not shown) on a workpiece (not shown) and during the penetration of the workpiece. In the described embodiment, it is therefore provided that the adjusting means 60 adjust the pressure of the high pressure supply 24 depending on the travel path, ie from the position of the piston 5. FIG. 4 shows the time characteristic of the position of the piston 5 together with the time course of the pressure of the high-pressure supply 24 set by the adjusting means 60. Starting from the retracted end position POSO of the piston 5, the piston 5 is moved in the working direction 11 up to the position POS1, in which the punching tool connected to the piston rod strikes the workpiece to be deformed. For this travel, the pressure of the high pressure supply 24 is set to a low value p1, which may be selected to be equal to that of the low pressure supply 26 in particular. The travel is detected by the displacement measuring system 62 and compared with a preset value, which corresponds for example to the distance of the punching tool in retracted end position of the piston 5 to the workpiece. If the piston has moved over the specified distance, then the punch meets the workpiece to be deformed. This takes place at the position of the piston indicated by POS1 in FIG. Then, the adjusting means 60 increase the pressure of the high-pressure supply 24 to a value p2, which is significantly higher than p1 and typically corresponds to the maximum pressure of the high-pressure supply 24. This high pressure is maintained for the further movement of the piston 5 in the working direction 11 until the punching tool attached to the piston rod 6 has penetrated the workpiece (position POS2 of the piston 5 in FIG. 4). Thus, the workload on the piston 5 decreases. If further movement of the piston 5 in working direction 11 to the position POS3 is provided, the adjusting means 60 reduce the pressure of the high-pressure supply 24 to a value p3 which is smaller than the pressure p2 and in particular equal to the pressure of the low-pressure supply 26. During the return movement of the piston 5 against the working direction 11 of the spool 30 blocks a further flow of hydraulic fluid from the high pressure supply 24 in the working pressure chamber 13. An energy-consuming volume flow of hydraulic fluid from the high pressure supply 24 is therefore prevented. The return movement is effected only by a volume flow of hydraulic fluid from the low pressure supply 26.
[0043] Das beschriebene Ausführungsbeispiel der Erfindung reduziert den Energiebedarf im typischen Einsatz mit wiederholtem Ausfahren und Rückfahren des Kolbens 5 erheblich. Dies geschieht zum einen dadurch, dass die Rückbewegung des Kolbens 5 entgegen der Arbeitsrichtung 11 grundsätzlich durch Hydraulikflüssigkeit von einer energiesparenden Niederdruckversorgung 26 bewirkt wird. Zum anderen wird durch die beschriebene, vom Verfahrweg und/oder der Arbeitslast des Kolbens 5 abhängige Hochdruckzuschaltung der Hochdruckversorgung 24 der Energiebedarf weiter reduziert. The described embodiment of the invention reduces the energy consumption in typical use with repeated extension and retraction of the piston 5 considerably. This is done on the one hand in that the return movement of the piston 5 against the working direction 11 is basically caused by hydraulic fluid from an energy-saving low-pressure supply 26. On the other hand, the energy requirement is further reduced by the described, depending on the travel and / or the workload of the piston 5 high-pressure connection of the high-pressure supply 24.

Claims

Ansprüche claims
1. Hydraulische Antriebsvorrichtung (1) mit einem in einem Zylinderraum (8) längs einer Arbeitsachse (10) verschiebbar geführten, einen mit Hydraulikflüssigkeit druckbeaufschlagbaren Arbeitsdruckraum (13) begrenzenden Kolben (5) und mit einem wenigstens abschnittsweise im Kolben (5) zwischen verschiedenen Steuerzuständen geführten Steuermittel (29) zur Steuerung des Durchflusses der Hydraulikflüssigkeit von einer Hochdruckversorgung (24) in den Arbeitsdruckraum (13) zum Bewegen des Kolbens in Arbeitsrichtung (11) und vom Arbeitsdruckraum (13) zu einem Rücklaufraum (15), dadurch gekennzeichnet, dass der dem Arbeitsdruckraum (13) abgewandte Bereich des Kolbens (5) einen Niederdruckraum (19) begrenzt, der im Betrieb der Vorrichtung von einer Niederdruckversorgung (26) für Hydraulikflüssigkeit derart druckbeaufschlagt ist, dass der Kolben (5) entgegen der Arbeitsrichtung (11) rückbewegt wird, wenn das Steuermittel (29) den Arbeitsdruckraum (13) mit dem Rücklaufraum (15) verbindet.1. Hydraulic drive device (1) with a in a cylinder chamber (8) along a working axis (10) slidably guided, a hydraulic fluid pressurizable working pressure chamber (13) limiting piston (5) and at least partially in the piston (5) between different control states Guided control means (29) for controlling the flow of hydraulic fluid from a high pressure supply (24) in the working pressure chamber (13) for moving the piston in the working direction (11) and the working pressure chamber (13) to a return space (15), characterized in that The working pressure chamber (13) facing away from the region of the piston (5) a low pressure space (19) limited, which is pressurized during operation of the device by a low pressure supply (26) for hydraulic fluid such that the piston (5) against the working direction (11) is moved back when the control means (29) connect the working pressure space (13) with the return space (15) t.
2. Antriebsvorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass der Niederdruckraum (19) unabhängig vom Steuerzustand des Steuermittels (29) von der Hochdruckversorgung (24) getrennt ist.2. Drive device according to claim 1, characterized in that the low-pressure chamber (19) is independent of the control state of the control means (29) separated from the high-pressure supply (24).
3. Antriebsvorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass Einstellmittel (60) vorgesehen sind, mittels welchen der Druck der Hochdruckversorgung (24) abhängig vom Verfahrweg längs der Arbeitsrichtung (11) des Kolbens (5) und/oder der Arbeitslast des Kolbens (5) einstellbar ist.3. Drive device according to claim 1 or 2, characterized in that adjusting means (60) are provided, by means of which the pressure of the high pressure supply (24) depending on the travel along the working direction (11) of the piston (5) and / or the workload of the piston (5) is adjustable.
4. Antriebsvorrichtung nach Anspruch 3, dadurch gekennzeichnet, dass die Einstellmittel (60) derart ausgebildet sind, dass der Druck der Hochdruckversorgung (24) zum Bewegen des Kolbens (5) aus seiner rückgefahrenen Endlage in Arbeitsrichtung (11) bis zur oder bis kurz vor der Aufnahme einer Arbeitslast einen Wert p1 und anschließend, insbesondere während der Arbeitslast, einen Wert p2 aufweist, wobei p1 < p2.4. Drive device according to claim 3, characterized in that the adjusting means (60) are designed such that the pressure of the high pressure supply (24) for moving the piston (5) from its retracted end position in the working direction (11) until or until shortly before a workload has a value p1 and then, in particular during the workload, has a value p2, where p1 <p2.
5. Antriebsvorrichtung nach Anspruch 4, dadurch gekennzeichnet, dass die Einstellmittel (60) derart ausgebildet sind, dass bei einem weiteren Bewegen des Kolbens (5) in Arbeitsrichtung (11) nach der Überwindung der Arbeitslast der Druck der Hochdruckversorgung (24) einen Wert p3 aufweist, wobei p3 < p2 und/oder p3 = p1.5. Drive device according to claim 4, characterized in that the adjusting means (60) are designed such that upon further movement of the piston (5) in the working direction (11) after overcoming the workload the pressure of the high-pressure supply (24) has a value p3, where p3 <p2 and / or p3 = p1.
6. Antriebsvorrichtung nach einem der vorherigen Ansprüche, dadurch gekennzeichnet, dass ein Wegmesssystem (62) zur Bestimmung des Verfahrweges des Kolbens (3) und/oder ein Lastmesssystem zur Bestimmung der Arbeitslast des Kolbens (3) vorgesehen ist.6. Drive device according to one of the preceding claims, characterized in that a displacement measuring system (62) for determining the travel of the piston (3) and / or a load measuring system for determining the working load of the piston (3) is provided.
7. Antriebsvorrichtung nach einem der vorherigen Ansprüche, dadurch gekennzeichnet, dass das Steuermittel (29) in dem Bereich, in dem es im Kolben (5) geführt ist, längs der Arbeitsrichtung (11) einen Druckraum (38) begrenzt, der mit dem Niederdruckraum (19) druckverbunden ist.7. Drive device according to one of the preceding claims, characterized in that the control means (29) in the region in which it is guided in the piston (5) along the working direction (11) delimits a pressure chamber (38) with the low-pressure chamber (19) is pressure-connected.
8. Antriebsvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Steuermittel (29) als ein wenigstens abschnittsweise im Inneren des Kolbens (5) längs der Arbeitsachse (10) geführter Steuerschieber (30) ausgeführt ist, welcher Steuerkanten (42, 43) aufweist, die zur Zusammenwirkung mit weiteren Steuerkanten (45, 46) am Kolben (5) ausgebildet sind, um den Durchfluss von Hydraulikflüssigkeit in den oder aus dem Arbeitsdruckraum (13) zu steuern.8. Drive device according to one of the preceding claims, characterized in that the control means (29) as an at least partially in the interior of the piston (5) along the working axis (10) guided control slide (30) is executed, which control edges (42, 43) which are designed to cooperate with further control edges (45, 46) on the piston (5) in order to control the flow of hydraulic fluid into or out of the working pressure chamber (13).
9. Antriebsvorrichtung nach Anspruch 8, dadurch gekennzeichnet, dass der Steuerschieber (30) einerseits in dem an den Niederdruckraum (19) angrenzenden Bereich des Kolbens (5) in einer zylindrischen Führungsöffnung (36) und andererseits im Zylindergehäuse (3) in einer weiteren zylindrischen Führungsöffnung (40) geführt wird, wobei die Führungsöffnungen (36, 40)den gleichen Durchmesser aufweisen.9. Drive device according to claim 8, characterized in that the spool (30) on the one hand in the low pressure space (19) adjacent region of the piston (5) in a cylindrical guide opening (36) and on the other hand in the cylinder housing (3) in a further cylindrical Guide opening (40) is guided, wherein the guide openings (36, 40) have the same diameter.
10. Antriebsvorrichtung nach Anspruch 8 oder 9, dadurch gekennzeichnet, dass eine Koppelstange (50) zur Betätigung des Steuerschiebers (30) derart vorgesehen ist, dass der Steuerschieber (30) mittels der Koppelstange (50) in Arbeitsrichtung (11) des Kolbens geschoben werden kann.10. Drive device according to claim 8 or 9, characterized in that a coupling rod (50) for actuating the control slide (30) is provided such that the control slide (30) by means of the coupling rod (50) in the working direction (11) of the piston are pushed can.
11. Hydraulische Antriebsvorrichtung nach Anspruch 10, dadurch gekennzeichnet, dass die Koppelstange (50) mit einem elektromechanischen Wandler (54) verbunden ist.11. A hydraulic drive device according to claim 10, characterized in that the coupling rod (50) with an electromechanical transducer (54) is connected.
12. Verfahren zum Betrieb einer hydraulischen Antriebsvorrichtung, insbesondere nach einem der vorhergehenden Ansprüche, mit einem in einem Zylinderraum (8) verschiebbar geführten Kolben (5), welcher einen Arbeitsdruckraum (13) begrenzt, wobei der Arbeitsdruckraum (13) zum Bewegen des Kolbens (5) in Arbeitsrichtung (11) mit Hydraulikflüssigkeit mit einem Hochdruck PH beaufschlagt wird, dadurch gekennzeichnet, dass zum Rückbewegen des Kolbens (5) entgegen der Arbeitsrichtung (11) ein Niederdruckraum (19), der durch einen dem Arbeitsdruckraum (13) abgewandten Bereich des Kolbens (5) begrenzt ist, mit einem Niederdruck PN beaufschlagt wird, wobei PN <= PH.12. A method for operating a hydraulic drive device, in particular according to one of the preceding claims, with a in a cylinder chamber (8) slidably guided piston (5) having a working pressure chamber (13) limited, wherein the working pressure chamber (13) for moving the piston (5) in the working direction (11) is acted upon by hydraulic fluid with a high pressure PH, characterized in that for returning the piston (5) against the working direction (11) a low-pressure space (19 ), which is bounded by a the working pressure chamber (13) facing away from the region of the piston (5), is subjected to a low pressure PN, where PN <= PH.
13. Verfahren nach Anspruch 12, dadurch gekennzeichnet, dass der Hochdruck der den Arbeitsdruckraum (13) druckbeaufschlagenden Hydraulikflüssigkeit abhängig vom Verfahrweg des Kolbens (5) und/oder der Arbeitslast des Kolbens (5) eingestellt wird.13. The method according to claim 12, characterized in that the high pressure of the working pressure chamber (13) pressurizing hydraulic fluid is adjusted depending on the travel of the piston (5) and / or the workload of the piston (5).
14. Verfahren nach Anspruch 12 oder 13, dadurch gekennzeichnet, dass der Niederdruckraum (19) ununterbrochen mit Niederdruck beaufschlagt wird.14. The method according to claim 12 or 13, characterized in that the low-pressure chamber (19) is continuously applied with low pressure.
15. Verfahren nach Anspruch 12, 13 oder 14, dadurch gekennzeichnet, dass der Hochdruck der den Arbeitsdruckraum (13) druckbeaufschlagenden Hydraulikflüssigkeit zum Bewegen des Kolbens (5) aus seiner rückgefahrenen Endlage in Arbeitsrichtung (11) bis zur oder bis kurz vor der Aufnahme einer Arbeitslast einen Wert p1 und anschließend, insbesondere während der Arbeitslast, einen Wert p2 aufweist, wobei p1 < p2, und für den Fall, dass ein weiteres Bewegen des Kolbens (5) in Arbeitsrichtung (11) nach der Überwindung der Arbeitslast vorgesehen ist, der Hochdruck einen Wert p3 aufweist, wobei p3 < p2 und/oder p3 = p1. 15. The method of claim 12, 13 or 14, characterized in that the high pressure of the working pressure chamber (13) pressurizing hydraulic fluid for moving the piston (5) from its retracted end position in the working direction (11) until or shortly before receiving a Workload has a value p1 and then, in particular during the workload, a value p2, where p1 <p2, and in the event that further movement of the piston (5) in the working direction (11) is provided after overcoming the work load, the High pressure has a value p3, where p3 <p2 and / or p3 = p1.
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EP2229537B1 (en) 2013-07-24
WO2010084043A1 (en) 2010-07-29
EP2229537B8 (en) 2013-10-30
US9121419B2 (en) 2015-09-01
DE102009005998A1 (en) 2010-08-05
CN102292554A (en) 2011-12-21
DE102009005998B4 (en) 2012-12-27
CN102292554B (en) 2014-07-09
US20110271667A1 (en) 2011-11-10

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