EP2280178B1 - Dispositif et méthode de contôle pour un ensemble piston-cylindre - Google Patents

Dispositif et méthode de contôle pour un ensemble piston-cylindre Download PDF

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Publication number
EP2280178B1
EP2280178B1 EP10012415A EP10012415A EP2280178B1 EP 2280178 B1 EP2280178 B1 EP 2280178B1 EP 10012415 A EP10012415 A EP 10012415A EP 10012415 A EP10012415 A EP 10012415A EP 2280178 B1 EP2280178 B1 EP 2280178B1
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EP
European Patent Office
Prior art keywords
pressure
piston
control
cylinder
sub
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German (de)
English (en)
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EP2280178A1 (fr
Inventor
Matthias Hahn
Ralph Lutz
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Laeis GmbH
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Laeis GmbH
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    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/008—Reduction of noise or vibration
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/555—Pressure control for assuring a minimum pressure, e.g. by using a back pressure valve

Definitions

  • the invention relates to a control device for a piston-cylinder arrangement, wherein the piston-cylinder arrangement has a cylinder and a piston which is accommodated at least partially in the cylinder and divides the cylinder interior along the cylinder axis into two subspaces, with one connected to a first subspace A valve assembly which occupies a closed position preventing leakage of fluid received in the first subspace from said subspace when the pressure in the fluid is less than a pressure control value set on the valve assembly and which opens into an open position permitting said outflow when the pressure in the fluid is greater than the set pressure control value, and a method for controlling such a piston-cylinder arrangement for carrying out a relative movement between the piston and cylinder, and the use of such a control device for a piston-cylinder arrangement of a hydrauli press.
  • Control devices of this type for a piston-and-cylinder arrangement such as EP 0 661 125 A1 , are known for example from the field of presses.
  • the term press in this context is to be understood as a collective term for differently operating hydraulic presses, by means of which processed by hydraulic force application products of various kinds, in particular can be transformed or manufactured. Examples of such presses are hydraulic stamping presses, impact shears, presses for the refractory and tile industry, presses for the production of salt products, products of lime sandstone, Tiles, etc.
  • the shaping of the products can be carried out such that two pressing dies, of which at least one is movable along a main axis of the press, are moved relative to each other and thus effect the forming process.
  • a press in the field of refractory industry for example, bulk loose material is compacted by the relative movement of the press dies in a die, which at least partially determines the shape of the compact produced by the pressing process.
  • the forming operation of the refractory press just described is shut down when either a certain distance has been traveled by the dies, a certain pressure in the master cylinders achieved or even if these two criteria are within a defined tolerance range.
  • piston-cylinder assemblies which are controlled by a control device of the type mentioned, not only used for the master cylinder or main ram, but also for secondary functions, which are also performed by means of the control device controlled piston-cylinder assemblies .
  • a secondary function is, for example, the process of a die wall of a die of a just presented press from the field of application of the refractory industry after completion of the pressing process. This involves the so-called shaping of the compact from the matrix, wherein the compact is supported against a stationary punch or a master cylinder, the die wall being moved relative to the main working axis by a movement effected by a piston-cylinder arrangement controlled by the control device and so the die is removed from the compact.
  • the shaping process can take place with respect to the press by a direction of action in the direction of the extending or in the direction of the retracting piston rod of the auxiliary cylinder.
  • the valve assembly connected to the first sub-chamber has the well-known function of self-weight of, for example, the pistons of such piston-cylinder assemblies to balance the coupled matrix.
  • a pressure control value is set to the valve assembly, the is at least as high as the pressure in a recorded in the first subspace fluid, which is caused by the weight of the female mold.
  • control devices of the type described above with respect to their durability and the durability of their controlled piston-cylinder arrangement in normal normal technical design are only slightly satisfactory, since after a relatively short period of operation damage to components of the control device itself as path detection systems or piping systems, or damage to the piston-and-cylinder arrangement, e.g. B. the welds and various other mechanical damage occur.
  • the thus observed unsatisfactory service life of components of the control device and controlled by her piston-cylinder assembly has the consequence that the corresponding parts must be designed reinforced, otherwise they must be costly to repair or replaced, and possibly the press during the Repair work can not be operated, thus resulting in production losses.
  • the invention has for its object to provide a control device for a piston-cylinder assembly of the type mentioned, which on the one hand itself has an increased durability when used in a press, but also the durability increases the controlled by her piston-cylinder arrangement, thus allowing a longer life of these parts of the press.
  • This invention is based on a detailed and detailed analysis of the dynamic pressure conditions throughout the hydraulic system of the control device and the piston-cylinder assembly.
  • mechanical stalls are responsible for the unsatisfactory durability of conventional control devices, which in turn are caused by mechanical vibrational excitations of the entire hydraulic system.
  • These mechanical vibration excitations arise after a recorded in one of the subspaces of the piston-cylinder assembly-fluid has been exposed by a movement of the piston along the cylinder axis of a pressure increase, and the outflow occurs against a flow resistance. This creates a pressure peak in the hydraulic system, which counteracts the movement of the piston causing this pressure increase. This causes a vibration excitation with a correspondingly high mechanical load for the entire assembly.
  • the pressure increase generated in the fluid by the pretensioning device provides for a pressure bias in the fluid.
  • this pressure bias the natural frequency of the hydraulic axis corresponding to the piston-cylinder arrangement controlled by the control device is increased, as a result of which pressure peaks otherwise occurring without damping are strongly damped and thus can no longer lead to damage.
  • control device controlled piston-cylinder arrangement for a secondary function for molding the compact from the die is used by moving the die
  • the forces acting in the forming area when using such a press are in the size range from 4000 kN to 36000 kN. If loose bulk material in the die is compressed and brought into shape by the use of such forces, a high pressure is also exerted transversely to the main working axis on the side walls of the die because the bulk material is pressed with great forces transversely to the main working axis against the side walls of the die. Between the compact and the Matrizenwandung, even after completion of the forming process, a correspondingly high static friction. This must be during the molding of the compact from the piston-cylinder arrangement be overcome. Therefore, a high force is required at least to trigger the Matrizenterrorism.
  • the usual method for shaping the compact also takes place.
  • a pressure is built up in a (second) subspace of the cylinder, for example on the piston side, which is sufficient when a critical size is reached to allow the force required to overcome the stiction to act on the die wall via the piston-cylinder arrangement.
  • the transition from static friction to sliding friction occurs abruptly, the piston moves and the molding process of the compact is initiated.
  • the volume flow of the fluid accompanying this acceleration is usually directed to a closed valve assembly having a set pressure control value which is higher than a pressure in the fluid which would be caused only by the die own weight.
  • the axis is finally decelerated via an uncontrolled pressure buildup in the first subspace, wherein a high set pressure control value causes greater delay values than a low set pressure control value. Since the valve arrangement is only opened by the pressure pulse resulting from the acceleration during this activation, it takes place Measure not sufficiently "fast", so that the uncontrolled pressure build-up in the first compartment creates a pressure peak that can increase up to six times the actual load pressure.
  • a pressure bias in the fluid in the first subspace and thus a large natural frequency of the hydraulic axis is provided. Vibration excitation can no longer occur or is so strongly damped that the negative effects for the machine are greatly reduced.
  • Another advantage of the control device according to the invention can be achieved by the pressure increase is just generated so that the pressure in the fluid is as close to or above the pressure control value. As long as the pressure remains below the pressure control value, the valve arrangement still remains in the closed position, but only a correspondingly low further pressure increase is necessary for the opening of the valve arrangement, ie, the valve arrangement is "virtually pre-opened". If the pressure is already above the pressure control value, the valve assembly is pre-opened. Of course, in this case, the movement of the piston should be carried out before the then occurring (albeit small) outflow of the fluid, the compressive bias is reduced too much. In both cases, in particular in the second case is additionally achieved that the response time of the valve assembly is significantly reduced compared to the case without pressure bias. Thus, the outflow of fluid from the first compartment can use faster, which reduces the height of the harmful pressure peak.
  • control device Another advantage of the control device according to the invention is that the pressure bias and the (quasi) pre-opening of the valve assembly can be prepared preparatory, that is not only prepared when the pressure increase is registered in the first subspace by sensors or other mechanisms. In this way, a very straightforward and less prone mechanism is provided, which prevents the vibration excitation or at least greatly reduces the harmful effects of vibration excitation.
  • the pressure bias value is equal to the pressure control value or only slightly greater than the pressure control value, for example by 0.1% or more, preferably 0.5% or more and in particular 1% or more.
  • the pre-opening of the valve assembly can be achieved satisfactorily.
  • a satisfactory deceleration of the axis is achieved.
  • the difference of pressure bias value and pressure control value is 20% or less, preferably 10% or less, and more preferably 5% or less of the pressure control value.
  • the outflow of the fluid remains sufficiently low, and the pressure bias does not degrade too quickly.
  • the valve arrangement is constructed in at least two stages, wherein it has a main stage whose release / blocking position corresponds to the open / closed position of the valve arrangement, and which can only assume its release position if a preliminary stage, at which the pressure control value is set, is open, wherein to take the release position after opening the precursor only a small pressure compared to the pressure control value is required.
  • the main stage is simulated by the pre-opening of the precursor (the pilot valve) a load. It is achieved that when opening the precursor to the opening of the main stage no longer a force that corresponds to the set pressure control value must be spent, so that the main stage immediately after their opening allows an outflow of the fluid at high flow rate.
  • the small pressure compared to the pressure control value corresponds to a non-hydraulic closing force provided in the closing mechanism of the main stage.
  • the inventively provided precursor and main stage are so hydraulically connected to the first subspace that the pressure in the fluid on the one hand on a load side of the main stage, the pressure of the blocking of the main stage counteracts, and on the other hand on a Steverseite the main stage, the pressurization of the release counteracts the main stage, as well as applied to the pre-stage, wherein preferably the length of at least partially having a bypass line connection between the first subspace and control side is greater than the length of a connection between the first subspace and load side.
  • Bypass here means a bypass of the load side of the main stage.
  • the length of the connection is not necessarily to be understood as a spatial length, but as a measure of the time required for a pressure propagation along the connection. For example, a throttle system causes an "extension" of the connection.
  • the main stage is thus closed and, as long as no flow forces occur, i. the axis is in rest position, even with pre-opened pre-stage hydraulically pressure-balanced, but by a non-hyraulically acting closing device, such as a spring locked.
  • the spring can expediently apply a pressure-converted spring force of 0.5-20 bar, preferably 1-10 bar and in particular 3-5 bar.
  • a pressure increase in the fluid caused by the movement of the piston reaches the load side of the main stage with a time lag in front of the pre-stage and also the control side of the main stage, with the effect that the main stage opens under the effect of lower pressure at the control side than at the load side and Outflow of the fluid can take place via the main stage.
  • the inventively provided load-independently generated pressure increase of the fluid from a storage system is effected, which is coupled via a line system to the first subspace / the valve assembly.
  • the production of the compression bias can be realized very easily cycle-independent.
  • a memory system possibly already present in such control devices can be used for this additional function.
  • Another advantage of the cycle-independently produced pressure bias is that vibration excitations are not transmitted to the damping circuit of the valve assembly and the main stage so show a stable transient response. A safe braking of the movement of the piston can be ensured.
  • a throttle system / throttle systems can be provided in the line system connecting the storage system to the pilot line, the pilot line and / or in a section of the bypass between the load and control sides of the main stage.
  • the pressure conditions remain unchanged in the static state of the fluid, however, in dynamic operation Volume reductions and a "lengthening" of connection lengths (see above) can be achieved, which allow a safe outflow of the fluid as desired carried out substantially completely over the main stage.
  • the pressure increase in the fluid can be effected not only in a control position but permanently.
  • the pressure control value set on the valve arrangement can be adjustable, that is to say in particular the maximum pressure bias value can be set.
  • This can be made possible on the one hand in a structurally simple embodiment by manual adjustment.
  • it is advantageous for the bundling of the entire control if the pressure control value is proportionally controllable, and in particular by a control device is set by a predetermined control voltage, wherein the control voltage is magnetically converted to a pressure control value.
  • Proportionally controllable means that the set pressure control value is proportional to the control voltage predetermined by the control device.
  • the response time of the valve assembly after bias only less than 50 ms, preferably less than 20 ms and in particular less than 5 ms. In this way, as already explained above, in addition, the height of a developing pressure peak can be reduced.
  • control device relate to the problem which arise at the beginning of a relative movement between the piston and cylinder of the piston-cylinder arrangement, in particular when the movement takes place with the sudden overcoming of the movement counteracting holding force, such as the breakaway torque Forming process of a compact from a die.
  • Another aspect of the invention relates to the continuation of a molding process thus started.
  • a supply of the second subspace required for a hydraulically caused relative movement of the piston in the direction of the first subspace with a hydraulic fluid in a first operating mode by means of a first hydraulic fluid flow outgoing from a pumping system at least in sections via a first conduit system and in a second mode by means of a second hydraulic fluid volume flow emanating from a storage system can take place at least in sections via a second line system, and means for switching over from the first to the second mode of operation are provided.
  • the pumping system must be available only during the activation of the first mode for the relative movement.
  • the means for switching comprises means for generating an increase in the pressure prevailing in the first conduit system, means for automatically releasing a connection between the storage system and the second compartment, when the pressure prevailing in the first conduit system exceeds a predetermined threshold, in a first control and means for maintaining this connection in a second drive.
  • the pressure increase is effected by throttling the first hydraulic fluid volume flow by means of a throttle valve.
  • the throttle valve is designed proportionally controllable, which allows a simple central control.
  • the throttle valve can fulfill even more functions, eg. B. cause a general switching the direction of the relative movement.
  • a throttling of the first hydraulic volume flow also causes a braking of the relative movement, thus, the first control can be characterized as a brake control.
  • the second drive can be characterized as a positioning drive, which is selected for switching (and which can be maintained during the second mode).
  • the pressure generated by the pumping system and prevailing in the first piping system is generally lower than the pressure present in the storage system.
  • the pressure threshold at which the release to the storage system takes place automatically is advantageously determined essentially by the pressure prevailing in the storage system, but is slightly above it.
  • a pressure already existing in the arrangement can be used as an essential threshold criterion, which makes structurally particularly simple implementations of the automatic release possible.
  • a significant advantage is achieved if the control device allows a transfer of an excess portion of the first hydraulic fluid flow into the storage system, this proportion is formed when the throttling of the first hydraulic fluid flow rate occurs with unchanged maintained first hydraulic fluid vofumen.
  • the pumping system reacts slower than a throttling effected in particular by means of a throttle valve. Failure to direct the resulting excess portion of the first hydraulic fluid flow into the storage system would in turn produce deleterious pressure spikes in the first conduit system.
  • the memory system is recharged in this way.
  • a preferred realization of the means for releasing the connection to the storage system provides a connection-valve arrangement which has a storage connection valve with a first connection connected to the first line system and a second connection connected to the second line system, the respective pressurization of the closing of the memory Counteracts the release valve, wherein the release is effected via an opening of the memory Zuschaltventils effected activation of a connection between the first port and the second port.
  • the release can be effected particularly easily, namely only by (automatic) opening of the memory Zuschaltventils.
  • the accumulator-Zuschaltventil has a third port, the pressure of which opposes the opening of the memory Zuschaltventils and is determined by a coupled to the third terminal valve group having a first valve which is open in the first control and a Release connection from the third port to the second conduit system.
  • a valve group required for closing the memory Zuschaltventils pressure can be applied in a simple design.
  • the sum of the effective areas of the first terminal and the second terminal is substantially equal to the effective area of the third terminal, and a Verschraceefernent, in particular in the form of a spring provided in the memory Zuschaltventil, the closed at balanced pressure conditions closing the Memory-Zuschaltventils effected with a force to compensate for a corresponding to the effective area of the first port converted compensation pressure is needed, and in which the predetermined threshold is determined by the sum of the prevailing pressure in the storage system and the compensation pressure.
  • a memory Zuschaltventil can be easily realized by a 2/2 way valve.
  • the balanced pressure conditions mean that a hydraulically determined equilibrium of forces prevails, ie the sum of the product of the first effective area with the pressure applied there and the product of the second effective area with the pressure applied there is equal to the product of the third effective area with the pressure applied there.
  • the closing element determines the position of the storage connecting valve.
  • connection to the storage system can be maintained particularly simply by virtue of the valve group having a second valve, which relieves the third connection when the position is open in the second control and makes it possible to maintain the connection between the storage system and the second compartment, in particular after one
  • the sensor provided on the memory connection valve was registered to release this connection.
  • This complete pressure relief quickly reduces the hydraulic resistance against the opening of the accumulator valve.
  • control device further means are provided which block the release of the connection to the storage system in a third drive.
  • This is advantageous if in the first line system, a higher pressure than that prevailing in the storage system should be built up to z. B. apply the necessary pressure to overcome a movement of the piston counteracting holding force. If the connection between the memory and the second subspace were also switched on in this case, such a pressure buildup would not be possible.
  • the third control can also be characterized as Druck
  • valve group has a third valve which, in the third open position by a connection of the third port with that of the first and second conduit system selected line system in which a higher pressure prevails, the Memory Zuschaltventil is blocked in the closed position, this selection of the piping system is in particular automatically by means of a coupled to both piping systems fourth valve.
  • the fourth valve may be formed as a simple shuttle valve
  • the pumping system can in principle be switched off.
  • the pumping system is merely switched away from this connection by means of a decoupling valve, and is available for further functions, for example for controlling further piston-cylinder arrangements.
  • the invention relates not only to a control device for a piston-cylinder arrangement, but also to a method for operating a piston-cylinder arrangement, wherein such a control method can be carried out in particular by means of a control device of the type just described.
  • a relative movement between the piston and cylinder of the piston-cylinder arrangement is effected in a first method step by means of a first hydraulic fluid volume flow generated by a pump system as a hydraulic fluid supply in a positive displacement control.
  • a transition from the positive displacement control into a throttle control and thus deceleration of the relative movement is initiated, wherein an excess portion of the first hydraulic fluid volume flow formed by the transition is replaced by an automatic release of a connection between the pumping system and a storage system is passed into the storage system, and in a third method step, a maintenance of this compound causes, and the Hydraulic fluid supply for the decelerated relative movement is effected by a second hydraulic fluid volume flow via the connection from the storage system.
  • This method combines the advantages, on the one hand z. B. Acceleration and rapid traverse of the piston in the piston-cylinder assembly in the displacement control with little conversion of hydraulic pressure energy to heat to be able to perform a braking movement of the piston from the storage system, whereby the pumping system for other tasks is free. It is also advantageous that the transition of the hydraulic fluid supply from pumping system to storage system is automatically initiated and occurs without discontinuities.
  • the throttling process begins at a braking time calculated by a control device.
  • both modes can merge into each other while maintaining a particularly efficient timing.
  • the automatic release takes place via a valve-connection valve controlled by a valve group and connected to the pumping system via a first line system connected to a first connection and to the storage system via a second line system connected to a second connection.
  • Valve of the valve group is opened in a first activation, in particular by non-activation of one / of the control device and openly causes the automatic release as soon as the pressure in the first conduit system exceeds a predetermined threshold caused by the throttling.
  • the switching between the hydraulic fluid supplies is carried out in a particularly uncomplicated manner, in that only the control of the valve group by the control device is to be controlled.
  • the maintenance of the connection between the storage system and the second subspace is expediently done by a second valve of the valve group is opened in a second control in particular by driving from the control device in this third step, a third port of the memory Zuschaltventils is relieved by this opening and thus the Maintenance is effected, wherein the control is triggered by the control device by registering the release in particular by a provided on the memory Zuschaltventil sensor and forwards a corresponding signal to the control device, while the first valve, in particular by driving from the control device is closed , and the first hydraulic fluid volume flow is switched away from the connection to the second subspace.
  • the second valve so the third port of the memory-Zuschaltventils is relieved, leaving it permanently open. Therefore, the first hydraulic fluid volume flow can then be switched to another destination.
  • the switching of the first and the second valve can take place, if immediately after release a sensor registers it and forwards a corresponding signal directly to the control device.
  • the relative movement of the piston is controlled by a throttle control fed from the storage system.
  • the relative movement is expediently carried out in one or the second control by throttling the second hydraulic fluid volume flow caused by the storage system brought to a halt, assuming a desired relative movement end position between the piston and cylinder. In this way, a positioning between the piston and cylinder can be achieved exactly to 0.01 mm.
  • a preparatory method step before the first method step in which a third valve of the valve group is opened in a third control, in particular by actuation of the control device, the first valve in particular being controlled by the control device and the second valve in particular, are closed by non-driving by the control device, and the release is prevented by blocking the memory Zuschaltventil in the closed position by connecting the third port with that of the first and second conduit system selected in which a higher pressure prevails, wherein in particular, the selection of this line system is effected automatically by means of a fourth valve coupled to both line systems.
  • the third control can thus be characterized as a pressure build-up control.
  • the invention provides a control method in which a pressure increase in the fluid to a predetermined pressure bias value is generated independently of a load acting on the piston in the direction of the first subspace.
  • the pressure in a hydraulic fluid received in the second subspace and thus the load can be increased until the movement of the piston in the direction of the first subspace is triggered.
  • the movement of the piston counteracts a load whose size is not known from the outset, as in the case of the molding process of a compact from a die, the movement is only on reaching the Use breakaway torque.
  • the pressure increase in the second subspace may be slow. Among other things, it can be prevented that the pumping system applies even more extensive pumping lines that can no longer be used.
  • the further method steps described above for the method and positioning of the piston can be carried out, in particular the preparatory method step being carried out before the movement of the piston is triggered and, in particular, switched by a control device to the displacement control by means of the first hydraulic fluid volume flow as soon as possible a measuring system has registered the triggering of the movement and has forwarded a corresponding signal to the control device.
  • control method and the proposed control devices can be useful for piston-cylinder assemblies of different types of use, especially if a relative movement between the piston and cylinder only after overcoming a holding force is possible.
  • control device for a hydraulic press, in particular in use of the refractory and tile industry, wherein the controlled by the control device piston-cylinder arrangement is used in particular for the already described as an example molding process of a compact from a die.
  • Fig. 1 shows the schematic structure of a hydraulic press 100 in a longitudinal sectional view.
  • the hydraulic press 100 has an upper spar 101 and a lower spar 102, wherein the upper spar 101 is arranged on traverse columns 107 supporting above the lower spar 102. Attached to the lower beam 102, a solid lower punch 104 projects vertically upwards.
  • a movable upper punch 103 is arranged, which together with the lower punch 104 forms the main working axis of the hydraulic press 100 and which can move by pressing onto the lower punch 104 a loose bulk material located between lower punch 104 and upper punch 103 to form a stone (compact) 110 , Laterally, the shape of the compact of one Die 105 determined.
  • the die 105 is firmly connected to a Matrizenwandung 106 which is movably mounted along the Verfahrklalen 107.
  • Piston-cylinder arrangements 109 whose pistons 9 remove the die 106 from the compact 110 in a molding process by a downward ejection movement with a piston force F K, serve to move the die wall.
  • the piston force F K In order to be able to trigger such a movement movement, however, the piston force F K must overcome a static friction force F H between the compact 110 and the side walls of the die 106.
  • Fig. 2a shows the components of the control device in a control scheme.
  • four piston-cylinder assemblies are provided, the piston 9 fixed to the die 20 (106 in Fig. 1 ) are connected.
  • Each piston 9 divides the interior of the cylinder of its associated piston-cylinder arrangement in two subspaces, here a cylinder annular surface space 8 (first subspace), which is penetrated by the piston 9 itself, and a cylinder-piston surface space 16 (second subspace).
  • a fluid 17 located in the cylinder annular surface space 8 counteracts under pressure via a cylinder annular surface 31 as an effective surface of an extension movement of the piston 9 out of the cylinder.
  • the fluid 17 is here a suitable hydraulic fluid.
  • a hydraulic fluid arranged in the cylinder-piston surface space 16 counteracts a retraction movement of the piston 9 via a cylinder piston surface 21 as an effective surface under pressure and may possibly cause an extension movement of the piston 9.
  • a control device comprising a pumping system 15 and a storage system 6, which are coupled via a plurality of valves and piping systems to the piston-cylinder assemblies and depending on the circuit of the plurality of valves Can change pressure conditions in the cylinder annular spaces and / or the cylinder piston surface areas and, of course, can cause extension or retraction movements of the piston 9. It is provided that the control of the valves and valve arrangements described in more detail below as well as the pumping system 15 via a control device 23 electronically.
  • the pumping system 15 is via a. sudschiagvcnti) 19 "', which prevents a return of a pump system 15 emanating from the first hydraulic fluid volume flow to the pumping system 15, connected to a designed as a directional control valve decoupling 14.
  • the first hydraulic fluid flow through a further check valve 19" on the storage system 6 to be conveyed into the storage system 6.
  • Fig. 2a the decoupling valve 14 is shown switched accordingly.
  • the first hydraulic fluid flow rate can be used for a further control 22, z. B.
  • circuit of the decoupling valve 14 passes the first hydraulic fluid flow to another directional control valve, the throttle valve 12, to a connection base A (first port) of a storage Zuschaltventils 29 and to a shuttle valve 5 (fourth valve), the latter being described later.
  • the first hydraulic fluid flow on the one hand can be blocked by throttling to zero crossing, or a connection to the piston-cylinder assemblies is established. This can be done on the one hand via a further check valve 19 'and a piping system 18 to the cylinder annular surface areas 8, or in the in Fig. 2c
  • the directional control valve 12 is proportionally controllable.
  • the load compensation valve 1 As follows. At the load compensation valve 1, a pressure control value is set, and an opening of the load compensation valve 1 and thus the outflow of the fluid 17 from the cylinder annular surface spaces 8 can only take place when the pressure in the fluid 17 exceeds the set pressure control value.
  • the set pressure control value is applied to the pilot valve 4, and the pilot valve 4 opens when the pressure in a voltage applied to the pilot valve 4 pilot control line 42 exceeds the set pressure control value.
  • the pilot line 42 is in turn connected via an aperture 13 with throttle effect with the piping system 18 and thus with the cylinder annular surface spaces 8. That is, in the static state, the pressure of the fluid 17 via the pilot line 42 is also at the pilot valve 4.
  • this pressure is applied not only to one of the closing of the main stage 2 counteracting load side of the main stage 2, but also on the opening of the main stage 2 counteracting control side of the main stage 2.
  • the pilot valve 4 itself is a known directly proportional controlled pressure relief valve, wherein the closing mechanism is magnetic and is controlled in proportion to a predetermined by the control device 23 control voltage.
  • the biasing device comprises in this embodiment, the storage system 6, the (second) line system 7 with a portion 62 and orifices 3.
  • the compressive bias in the cylinder in the Ring lake linen 8 and the pipe system 18 received fluid 17 takes place from the storage system 6 along in Fig. 2b illustrated arrows a - I.
  • the first line system 28 has a connection to both the storage connection valve 29 and the shuttle valve 5.
  • the memory system 6 is, as in the Figures 2 and in particular 3 can be seen, connected via the second conduit system 7 to an annular surface B of the storage Zuschaltventils 29.
  • the memory Zuschaltventil 29 itself is a 2/2 way installation valve, in which the effective area of the connection to the base A of the so-called 100% effective area corresponds to Effective area of the connection to the annular surface B corresponds to the so-called 50% effective area, and the effective area of the further contained connection to the control surface C corresponds to the so-called 150% effective area.
  • open-close valve 25 means that the valve is open in the basic circuit, that is to say not activated, and is closed when actuated by the control device 23. Intermediate positions are not provided. Accordingly, the open-close valves 24 and 26 are opened by driving the control device 23, while they are closed in the basic position.
  • Each of the valves 24, 25 and 26 opens open a connection to the control surface C of the memory Zuschaltventils 29 ago. When the valve 25 is open, this connection couples to the second line system 7 and thus to the pressure in the storage system 6.
  • connection established by the open valve 24 couples to a tank, thus completely relieving the control surface C of the store connection valve 29.
  • the connection through the open valve 26 is coupled to the shuttle valve 5. This is designed so that it couples the control surface C of the memory Zuschaltventils 29 to the first conduit system 28 when the pressure in the first conduit system 28 is greater than the pressure in the second conduit system. 7 and conversely, the control surface C couples to the second conduit system 7 when the pressure in the second conduit system 7 is greater than the pressure in the first conduit system 28.
  • valves 24, 25, 26 are open, while the other two are closed.
  • a brake control first activation
  • the valve 25 is opened while the valves 24 and 26 are closed.
  • This control corresponds to the basic circuit of the three valves 24, 25 and 26, since none of them is controlled by the control device 23.
  • second control the valve 24 is activated and opened, while the valve 25 controlled and closed and the valve 26 is not activated and closed.
  • a pressure build-up control third control
  • the valve 26 is activated and opened, while the valve 24 is not activated and closed and the valve 25 is activated and closed.
  • the memory connection valve 29 is always closed.
  • a sensor 30 is provided on the memory Zuschaltventil 29, which communicates to the control device 23, whether the memory Zuschaltventil 29 is opened or closed.
  • the sensor 30 directly signals the control device 23 when the memory connection valve 29 opens in the brake control.
  • Wegmeßsystem 27 signals the position of the die 20 and thus also the position of the piston 9 relative to the piston-cylinder assemblies to the controller 23.
  • the position measuring system 27 directly signals the control device 23 when, during the molding process, the movement of the die 20 or the piston 9 abruptly begins after overcoming the static friction between the compact and the die 20.
  • a coupled to the piping system 18 pressure relief valve is provided, the z. B. in emergencies for a pressure relief of the fluid 17, as well as another provided via a check valve 19 to the supply line to the cylinder piston surface spaces 16 coupled tank from which the cylinder piston surface spaces 16 may possibly absorb by suction hydraulic fluid, thus itself can not form a vacuum in the cylinder-piston surface spaces 16 in an extension movement of the piston 9.
  • the pressure bias is generated in the fluid 17 in the cylinder annular surface spaces 8 and the piping system 18 by pressure increase from the storage system 6. This is indicated by the arrows a - I in Fig. 2b shown.
  • the pressure in the fluid 17 is thus brought to a predetermined pressure bias value which is set equal to the pressure control value set on the pilot valve 4 so that the pilot valve 4 is opened when the pressure bias is generated, but the main stage of the load compensation valve 1 is still closed remains, but "quasi-pre-opened", since the opening is now effected by only a relatively small additional pressure increase (corresponding to the converted 4 bar spring force) in the fluid 17.
  • the 2/2 way valve 12 already on the in Fig.
  • the die 20 should be moved into a removal position. This initially takes place in a displacement control by means of the first hydraulic fluid volume flow starting from the pumping system 15.
  • the pumping power of the pumping system 15 is thereby switched by the control device 23 to a power value which can be carried out via a corresponding first hydraulic fluid volume flow, the movement of the die 20 in accordance with a speed value calculated by the control device 23.
  • the pressure in the first line system (28) is lower than the pressure in the storage system 6.
  • the movement could now be brought to an end by reducing the first hydraulic fluid volume flow on the pump system side. According to the invention, however, a different continuation of the movement is provided.
  • the valve group is controlled in the brake control, so that the in Fig. 3b shown pressure situation at the memory Zuschaltventil 29 results.
  • base area A of the storage connection valve 29 is connected to the first line system 28 and ring area B to the second line system 7, here represented by the arrows a, b and c to e.
  • the control surface C is also connected to the second conduit system 7 as indicated by arrows c, d, e ', f to h in FIG Fig. 3b shown.
  • the memory Zuschaltventil 29 is closed, but can be opened as soon as the pressure in the first conduit system 28 increases to the pressure in the storage system 6 plus the 4 bar in this embodiment to overcome the spring force.
  • the control device 23 controls the 2/2 way valve 12 so that the first hydraulic fluid volume flow is throttled. There is the transition from the displacement control in a throttle control, and the Matrizenterrorism is decelerated accordingly. In this case, the first hydraulic fluid volume flow starting from the pumping system 15 remains adjusted to the same value. By throttling with constant pumping power, the pressure in the firstöns'28 increases. If the pressure in the first line system 28 reaches the pressure threshold just mentioned, the memory connection valve 29 opens, and the result is the in Fig. 3c illustrated situation.
  • this labile state of equilibrium of the storage connection valve 29 is now terminated, and provision is made for a hydraulic fluid supply of the movement movement from the storage system 6.
  • the sensor 30 directly registers the opening of the accumulator-connecting valve 29 and signals this information to the controller 23.
  • the controller 23 controls the valve group in the positioning drive.
  • the resulting situation is in Fig. 3d shown.
  • the valve 25 By closing the valve 25, the connection of the control surface C to the storage system 6 and the first conduit system 28 is capped.
  • the control surface C is relieved to the tank, as indicated by the arrows a to e in Fig. 3d displayed.
  • a VJUetzaufwalement of the die 20 to a level for a further cycle can then be carried out analogous to the corresponding phase of the molding process, of course, the 2/2 way valve is switched for the upward movement in a straight position.
  • This is again the acceleration and Rapid traverse of the die 20 in one of the pumping system 15 supplied Verdränger facedung, the transition of Verdränger facedung in a throttle control with subsequent switching of the hydraulic fluid supply, which in turn takes place for positioning from the storage system 6.
  • the overall sequence controlling control device 23 is an electronic control which is designed so that they can not only cause the same time sequence of the functional sequences with the same traversing speeds and travel paths, but rather the temporal sequence of the functional sequences can vary in which Traversing speeds and travel paths or the braking time can be switched from cycle to cycle differently. These traversing speeds, travels and the braking time can be calculated on the one hand by the electronic controller 23, on the other hand is also thought of the possibility that they can be entered manually.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Presses (AREA)
  • Fluid-Damping Devices (AREA)

Claims (15)

  1. Dispositif de commande destiné à un système piston-cylindre, dans lequel le système piston-cylindre présente un cylindre et un piston (9) logeant au moins partiellement dans le cylindre et divisant l'intérieur du cylindre le long de l'axe du cylindre en deux espaces partiels (8, 16), et comporte un système de soupape (1) relié au premier espace partiel (8), lequel système de soupape passe dans une position de fermeture empêchant l'écoulement d'un fluide (17) contenu dans le premier espace partiel (8) hors dudit espace partiel (8) lorsque la pression du fluide (17) est inférieure à une valeur de contrôle de pression pré-établie pour le système de soupape (1), et s'ouvre pour passer à une position d'ouverture permettant cet écoulement lorsque la pression du fluide (17) est supérieure à la valeur de contrôle de pression pré-établie,
    caractérisé par un dispositif de précontrainte qui est couplé au système de soupape (1) et au premier espace partiel (8) et qui prépare l'amortissement d'une charge de pression sous forme d'une brusque augmentation de pression du fluide (17) déclenchée par un déplacement du piston (9) causé par une charge agissant sur le piston (9) en direction du premier espace partiel et provoquée par le relâchement d'un volume de compression formé dans le deuxième espace partiel (16), lequel dispositif de précontrainte permettant de produire une augmentation de pression du fluide (17) indépendamment de la charge, pour le faire passer à une valeur de précontrainte de pression prédéterminée.
  2. Dispositif de commande selon la revendication 1, dans lequel la valeur de précontrainte de pression est essentiellement égale à la valeur de contrôle de pression, ou bien est supérieure de 0,1 % ou plus, de préférence de 0,5 % ou plus et notamment de 1 % ou plus, à la valeur de contrôle de pression.
  3. Dispositif de commande selon l'une des revendications 1 ou 2, dans lequel la différence entre la valeur de précontrainte de pression et la valeur de contrôle de pression est de 20 % ou moins, de préférence de 10 % ou moins et notamment de 5 % ou moins de la valeur de contrôle de pression.
  4. Dispositif de commande selon l'une des revendications 1 à 3, dans lequel le système de soupape (1) est constitué en au moins deux étages, en présentant un étage principal (2) dont la position de libération/verrouillage correspond à la position d'ouverture/fermeture du système de soupape (1), et qui ne peut adopter la position de libération que lorsqu'un étage préliminaire (4), dans lequel est établie la valeur de contrôle de pression, est ouvert, en sachant que seule une pression inférieure à la valeur de contrôle de pression est nécessaire pour pouvoir adopter la position de libération après l'ouverture de l'étage préliminaire (4).
  5. Dispositif de commande selon la revendication 4, dans lequel l'étage préliminaire (4) et l'étage principal (2) sont reliés au premier espace partiel (8) par voie hydraulique de manière que la pression du fluide (17) s'applique d'une part sur un côté charge de l'étage principal (2) dont la pressurisation agit à l'encontre du verrouillage de l'étage principal (2), et d'autre part, sur un côté commande de l'étage principal (2) dont la pressurisation agit à l'encontre de la libération de l'étage principal (2), ainsi que sur l'étage préliminaire (4), dans lequel de préférence la longueur d'un raccord présentant au moins par sections une conduite de contournement est plus grande entre le premier espace partiel (8) et le côté commande que la longueur d'un raccord entre le premier espace partiel (8) et le côté charge.
  6. Dispositif de commande selon l'une des revendications 1 à 5, dans lequel le dispositif de précontrainte présente un système de stockage (6) permettant de produire l'augmentation de pression par le biais d'un système de conduite (7).
  7. Dispositif de commande selon les revendications 5 et 6, dans lequel le système de conduite (7) présente une section (62) qui est reliée à une conduite de commande pilote (42) reliant l'étage préliminaire (4) et le côté commande de l'étage principal (2).
  8. Dispositif de commande selon l'une des revendications 5 à 7, dans lequel la conduite de contournement et/ou la conduite de commande pilote (42) et/ou la section (62) présente(nt) un système d'étranglement (13, 3).
  9. Dispositif de commande selon l'une des revendications 1 à 8, dans lequel l'augmentation de pression produite par le dispositif de précontrainte est durable dans un état statique du fluide (17) et, dans l'état statique notamment, la pression du fluide (17) est égale à la pression régnant dans le système de stockage (6).
  10. Dispositif de commande selon l'une des revendications 1 à 9, dans lequel la valeur de contrôle de pression est réglable, et ce de manière notamment manuelle.
  11. Dispositif de commande selon l'une des revendications 1 à 9, dans lequel la valeur de contrôle de pression est réglable et à commande proportionnelle, dans lequel notamment la commande de la valeur de contrôle de pression est réalisée notamment par l'intermédiaire d'une tension de commande prédéterminée par un organe de commande (23) et le réglage de la valeur de contrôle de pression sur le système de soupape (1)/l'étage préliminaire (4) s'effectue par voie magnétique.
  12. Dispositif de commande selon l'une des revendications 1 à 11, dans lequel le temps de réponse du système de soupape (1) se situe dans la plage allant de 1 à 50 ms, de préférence de 1 à 20 ms et notamment de 1 à 5 ms.
  13. Procédé de commande d'un système piston-cylindre, comportant notamment un dispositif de commande selon l'une des revendications 1 à 12, dans lequel le système piston-cylindre présente un cylindre et un piston (9) logeant au moins partiellement dans le cylindre et divisant l'intérieur du cylindre le long de l'axe du cylindre en deux espaces partiels (8, 16), et le premier espace partiel (8) est relié à un système de soupape (1) qui passe dans une position de fermeture empêchant l'écoulement d'un fluide (17) contenu dans le premier espace partiel (8) hors dudit espace partiel (8) lorsque la pression du fluide (17) est inférieure à une valeur de contrôle de pression pré-établie pour le système de soupape (1), et qui s'ouvre pour passer à une position d'ouverture permettant cet écoulement lorsque la pression du fluide (17) est supérieure à la valeur de contrôle de pression pré-établie, caractérisé en ce que, indépendamment d'une charge agissant sur le piston (9) dans la direction du premier espace partiel (8), il se produit une augmentation de pression du fluide (17), qui atteint une valeur de précontrainte de pression prédéterminée, de telle manière que l'on obtient la préparation de l'amortissement d'une charge de pression sous forme d'une brusque augmentation de pression du fluide (17) déclenchée par un déplacement du piston (9) causé par une charge agissant sur le piston (9) en direction du premier espace partiel et provoquée par le relâchement d'un volume de compression formé dans le deuxième espace partiel (16).
  14. Procédé selon la revendication 13, dans lequel, de surcroît, la pression d'un fluide hydraulique contenu dans le deuxième espace partiel (16) et ainsi, la charge, peut subir une augmentation sous l'effet d'un débit de fluide hydraulique produit par un système de pompe (15), jusqu'à ce qu'il se déclenche un mouvement du piston (9) en direction du premier espace partiel (8) notamment en surmontant une force de maintien exercée à l'encontre de la charge
  15. Utilisation d'un dispositif de commande selon l'une des revendications 1 à 12 pour un système piston-cylindre d'une presse hydraulique notamment destinée à l'industrie des réfractaires et du carrelage, dans lequel le système piston-cylindre est employé notamment dans un processus de démoulage d'une pièce pressée à partir d'un produit en vrac hors d'une matrice co-constituante du moule de la pièce pressée, dans un axe de travail auxiliaire.
EP10012415A 2005-09-12 2006-08-14 Dispositif et méthode de contôle pour un ensemble piston-cylindre Active EP2280178B1 (fr)

Applications Claiming Priority (2)

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DE102005043367.7A DE102005043367B4 (de) 2005-09-12 2005-09-12 Steuervorrichtung und Steuerverfahren für eine Kolben-Zylinder-Anordnung
EP06776836.6A EP1924773B1 (fr) 2005-09-12 2006-08-14 Procédé et dispositif de commande d'un système piston-cylindre

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CN (1) CN101305189B (fr)
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DK (1) DK1924773T3 (fr)
ES (2) ES2397822T3 (fr)
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DK1924773T3 (en) 2019-03-11
ES2710673T3 (es) 2019-04-26
CN101305189A (zh) 2008-11-12
EP1924773A1 (fr) 2008-05-28
CN101305189B (zh) 2011-01-12
PT1924773T (pt) 2019-03-21
JP2009508060A (ja) 2009-02-26
JP4885223B2 (ja) 2012-02-29
US8215108B2 (en) 2012-07-10
EP2280178A1 (fr) 2011-02-02
PL1924773T3 (pl) 2019-05-31
ES2397822T3 (es) 2013-03-11
DE102005043367B4 (de) 2016-09-08
EP1924773B1 (fr) 2018-12-05
DE102005043367A1 (de) 2007-03-15
WO2007031163A1 (fr) 2007-03-22
US20100212490A1 (en) 2010-08-26
TR201900650T4 (tr) 2019-02-21

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