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EP0559651B1 - Machine a entrainement hydraulique avec deux cylindres d'entrainement - Google Patents

Machine a entrainement hydraulique avec deux cylindres d'entrainement Download PDF

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Publication number
EP0559651B1
EP0559651B1 EP91915910A EP91915910A EP0559651B1 EP 0559651 B1 EP0559651 B1 EP 0559651B1 EP 91915910 A EP91915910 A EP 91915910A EP 91915910 A EP91915910 A EP 91915910A EP 0559651 B1 EP0559651 B1 EP 0559651B1
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EP
European Patent Office
Prior art keywords
pressure
control
drive
valve
pressure chamber
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EP91915910A
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German (de)
English (en)
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EP0559651A1 (fr
Inventor
Eckehart Schulze
Luciano Zanolini
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Individual
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    • 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
    • B30B15/24—Control arrangements for fluid-driven presses controlling the movement of a plurality of actuating members to maintain parallel movement of the platen or press beam

Definitions

  • the invention relates to a hydraulically driven machine for processing a sheet metal workpiece by cold forming, according to the preamble of claim 1.
  • a hydraulically driven machine for processing a sheet metal workpiece by cold forming, according to the preamble of claim 1.
  • Such a machine is known from US-A-2 211 692.
  • Such machines are known, for example, as bending machines, in which the sheet metal workpiece is arranged between a lower tool and an upper tool which can be moved up and down relative to the latter, for the drive of which two drive cylinders, which are arranged at a lateral distance from one another and are designed as differential cylinders, are provided, the pistons of which have piston rods emerging from the cylinder housings with which the upper tool is connected to compensate for slight differences in stroke of the pistons via uniaxial joints, the joint axes of which are perpendicular to the plane marked by the central axes of the drive cylinders, the ratio F 1 / F 2 of the surfaces F 1 and F 2 the piston, with which they each delimit an upper drive pressure chamber against a lower drive pressure chamber axially penetrated by the piston rod, through their common or alternative - valve-controlled - pressurization and / or - relief of the workpiece directed rapid feed movements and load feed movements, and rapid return movements directed away from the workpiece can be controlled, has a value between 5 and 20, with
  • This weight is sufficient to achieve a sufficient pressure in the downward rapid feed operation of the two drive cylinders of the machine - with the upper drive pressure chamber of the respective drive cylinder relieved of pressure in their lower drive pressure spaces, below which the pressure medium is sufficiently quick in the usual dimensions of the line cross sections and the control valves the lower drive pressure chambers of the drive cylinders can flow away in order to achieve the required speeds of the rapid feed movements and to be able to regulate them by suitable throttling of the outflow cross-sections, without having to "help" the rapid downward movements of their pistons by increasing the pressure in the upper drive pressure chambers of the drive cylinders, due to the area ratio F1 / F2 would require higher delivery rates of the pump of the pressure supply unit.
  • hydraulic drives for bending machines are usually provided with measuring systems implemented using glass scales, which measure the absolute values of the positions of the pistons at any moment enable capture.
  • measuring systems are very expensive and also susceptible to temperature influences and / or environmental conditions in general.
  • the object of the invention is therefore to improve a machine of the type mentioned in such a way that not only is the electro-hydraulic effort required to control its movement reduced, but also shorter cycle times of processing can be achieved.
  • the follow-up valves provided as part of the position control loops for the two drive cylinders, designed as 3/3-way valves, which work with pulse-controlled position setpoint specification and mechanical position actual value feedback, with the position setpoint If electrical AC or stepper motors are used, which allow an incremental position setpoint specification, the motion control of the drive cylinders can be easily achieved by controlling the electric motors at the same frequency, the mechanical actual position value feedback ensuring that the overrun Control valves quickly enough in the sense of the respective direction of movement can be controlled. Provided the pressure supply unit has sufficient performance, the two follow-up control loops can be operated with optimally high loop gain.
  • the permanent connection of the high-pressure outlet of the pressure supply unit to the lower drive pressure chamber of the respective drive cylinder provides effective protection against dangerous "falling" of the drive cylinder pistons or the upper tool of the machine, at least in the event of malfunctions in the electrohydraulic control unit.
  • the respective overrun control valve automatically returns to its blocking state due to the mechanical feedback of the actual position value, so that an adequate safeguard against "falling" of the upper tool is also guaranteed.
  • the high-pressure pump of the pressure supply unit is designed for the maximum delivery capacity provided in accordance with claim 2, it being advantageous from the point of view of minimizing the electrical connection power if, as provided in accordance with claim 3, the high-pressure pump of the Pressure supply unit is designed as a pressure-controlled pump, for example a pump, the flow rate of which is inversely proportional to the outlet pressure generated at its outlet. Alternatively or in combination with this, it can also be sufficient or additionally advantageous if a pressure relief valve designed according to claim 4 is provided, which can also be advantageous as a safety measure in combination with a pump regulated according to claim 2.
  • the outflow valve provided in the context of the electrohydraulic control unit can be designed as a solenoid valve controlled according to the features of claim 5, which is particularly advantageous in terms of simple control.
  • Such a compensation device can be implemented in a simple manner according to the construction principle according to the features of claim 9 and in a special embodiment according to that of claim 10.
  • the design of the compensation device according to claim 12 has the advantage of significantly less influence on the hydraulic rigidity of the drive compared to that of claim 11, but requires a somewhat increased technical effort to implement.
  • the machine can be largely secured against damage which could result from an inexactly synchronous feed of the two drive cylinder pistons.
  • this encoder system conveys the function provided according to claim 14, so that its output signals are a direct measure of the so-called tracking error, ie the distance by which the actual position value lags behind the set position setpoint, then this encoder system is in combination with the setpoint - Presetting system also as electronic Position actual value measuring system can be used, which provides a CNC-controlled machine with the electronic information required for this about the actual position of the upper tool.
  • the output signals of such a tracking error measuring system can also be advantageously used for a type of control of the position setpoint specification provided in accordance with claim 15 and thus gentle operation of the machine can be achieved.
  • 1, 2 and 3 generally designated 10, is a machine of the type in which, by means of a force-controlled lowering of an upper tool 11 relative to a lower tool 12 fixed to the machine frame, a workpiece 13, e.g. a steel sheet, which rests on the lower tool 12, is pressed into a desired shape, which is determined by the design of the lower tool 12 and the upper tool 11, which is complementary in cross section to the lower tool.
  • a workpiece 13 e.g. a steel sheet
  • the machine 10 comprises a machine frame, generally designated 14, with two C-shaped side walls 17 and 18, which are arranged symmetrically with respect to a vertical transverse center plane 16 of the machine frame 14 and which, as shown in FIG. 1, are arranged at a lateral clearance b from one another and through a base part 19, as it were a base of the machine frame 14, are connected to one another, which extends between the lower, horizontal transverse legs 21 and 22 of the overall C-shaped side walls 17 and 18, which are integrally connected to upper ones via vertical, columnar yoke legs 23 and 24 , horizontal transverse legs 26 and 27 of the C-shaped side walls 17 and 18 are formed contiguously.
  • a hydraulic drive cylinder 31 or 32 is fixedly mounted with the vertical course of the respective central longitudinal axis 28 or 29, the pistons of which are labeled 33 and 34, respectively, emerging from the cylinder housings 36 and 37 downwards Have 38 and 39 respectively.
  • These drive cylinders 31 and 32 are designed as double-acting differential cylinders, in which an upper drive pressure chamber 43 and 44 against a lower drive pressure chamber 46 and 47, respectively, by means of a piston flange 41 or 42 sealed against the cylinder housing 36 or 37 by means of a piston-fixed ring seal is delimited so as to be pressure-tight and movable, by means of which, by means of an electrohydraulic control unit, which is designated in total by 48, it acts upon the outlet pressure P of a pressure supply unit, which is designated in total by 49, and connects it to its - pressure-less - reservoir 51 directed towards the workpiece 13 in rapid downward movements of the upper tool 11 articulated with the piston rods 38 and 39 of the two drive cylinders 31 and 32, load feed movements of the same, by means of which the deformation of the workpiece 13 is achieved, and rapid retraction movements of the upper tool 11 in the sense of lifting the same from Workpiece 13 and return to an upper end position are controllable.
  • the total weight of the moving parts of the bending machine 10 - essentially its upper tool 11 and the pistons 38 and 39 of the two drive cylinders 31 and 32 articulated to it - is in a typical dimensioning 10 kN.
  • the delivery capacity of the pressure supply unit 49 is adapted to this dimensioning of the drive cylinders 31 and 32 in such a way that in the load-down feed operation, ie in the operating state of the bending machine 10 in which the workpiece 13 is deformed, a maximum value of the feed speed 30 mm / s is possible.
  • the central functional element of the subunit 48 'of the electrohydraulic control unit 48 is a follow-up control valve, designated overall by 61, for the structural and functional explanation of which reference is also made to the relevant details in FIG. 4.
  • the overrun control valve 61 by means of which the direction and speed of the possible movements of the piston 33 of the drive cylinder 31 can be controlled - rapid feed and load feed movements directed towards the workpiece 13 and rapid upward movements directed away from the workpiece 13 - , its function is a 3/3-way valve, which is connected to the high pressure outlet 62 of the pressure supply unit 49, first (P-) supply connection 63 and a second, connected to the unpressurized reservoir 51 of the pressure supply unit 49 (T-) supply connection 64 and a single control output 66, which on the one hand via a check valve 67, which is due to relatively higher pressure at the control output 66 of the
  • the follow-up control valve 61 is acted upon in the opening direction and, on the other hand, is connected to the control connection 69 of the drive cylinder 31 via a throttle 68, which is connected in parallel with this and designed as an orifice, via which the upper drive pressure chamber 43 of the drive cylinder 31 can be pressurized or depressurized Reservoir 51 of the pressure
  • the overrun control valve 61 has a neutral position O, a blocking position, in which its control output 66 is blocked both against its P supply connection 63 and against its T supply connection 64.
  • the rapid and the load feed operation of the drive cylinder 31 is assigned the functional position of the follow-up control valve 61, which is denoted by I in FIGS. 3 and 4, in which the P supply connection 63 of the valve 61 with its control output 66 and thus also with the Control port 69 of the drive cylinder 31 hydraulically is connected while the T supply connection 64 is blocked against the control output 66.
  • the overrun control valve 61 is - for the purpose of explanation - according to the semi-schematic representation of FIG. 4 provided as a slide valve, the "piston" 72 of which is represented by the 3/3-way valve symbol. It is designed as a proportional valve, which, seen from its blocking basic position O, with an increasing displacement of its valve piston 72 to the "left", ie in the sense of utilizing the functional position II - actuation of the drive cylinder 31 in the upward direction - releases an increasingly larger cross section of the flow thread 73, via which pressure medium can flow out of the upper drive pressure chamber 43 of the drive cylinder 31 to the unpressurized reservoir 51 of the pressure supply unit 49, and with increasing displacement of its valve piston 72 to the "right”, ie transition to functional position I - Actuation of the drive cylinder 31 in the downward direction - releases increasingly larger cross sections of the flow path 74, via which pressure medium can flow from the pump 57 and also from the lower drive pressure chamber 46 of the drive cylinder 31 to the upper drive pressure chamber 43 of the
  • the housing 75 of the follow-up control valve 61 which is only indicated schematically, has a block-shaped central section 76 with a central bore 77, in which a hollow shaft 79 is mounted, which can be rotated about its central longitudinal axis 78 and displaceable along this axis Figure 4 right end, which protrudes from the housing 75, is provided with a drive pinion 80, with which the output gear 81 of an electric motor 82 meshes, and provided at its other end with an internal thread 83 is in meshing engagement with a threaded spindle 84, which is also rotatable about the central axis 78, but is axially immovably mounted on the housing 75 of the follow-up control valve 61, from which it projects with a free end portion 84 ', on which in turn a pinion 86 is arranged, which is in meshing engagement with a rack 87 which, as can be seen in FIG. 3, is coupled in motion to the upper tool 11 and carries out its downward and upward movements, the rack 87
  • This threaded spindle 84 and the rack 87 are the functionally essential elements of a mechanical feedback device, by means of which the position of the upper tool 11 is "reported back" to the relief control valve 61.
  • a generally designated 88 yoke-shaped valve actuating member which has two parallel yoke legs 89 and 91, which are parallel to the central longitudinal axis 78 of the follow-up valve.
  • Control valve extending guide rod 92 which passes through a radially lateral guide bore 93 of the block-shaped, central housing part 76, are firmly connected to one another and are axially supported on the opposite sides of the valve piston 72 via an actuating pin 94 and 96, wherein this support of the yoke legs 89 and 91 on the actuating pins 94 and 96 or the valve piston 72 is fully positive.
  • the two yoke legs 89 and 91 are aligned with each other, with the central longitudinal axis 78 of the valve housing 75 coaxial bores 97 and 98, the diameter of which is slightly larger than the outer diameter of the hollow shaft 79, so that this with a sufficient for their smooth rotation by this game Bores 97 and 98 of the yoke legs 89 and 91 of the valve actuating member 88 can pass through.
  • valve actuation member 88 is axially free of play between radial driving flanges 102 and 103 of the hollow shaft 79 via ball bearings 99 and 101, which impart smooth rotation of the hollow shaft 79 relative to the valve actuation member 88.
  • the electric motor 82 is designed as a motor with a reversible direction of rotation, for example as a stepper motor or as an AC motor, that is to say as a pulse-controlled motor, which receives output pulses from an electronic control unit 100 received at a first supply connection 105 in the clockwise direction represented by the arrow 104 and by one second supply connection 106 received output pulses of the electronic control unit 103 is driven in the counterclockwise direction represented by arrow 107, the clockwise direction being indicated by arrow 108 is related.
  • the electric motor 82 it is further assumed that its armature, which is connected to the driven gear 81 in a rotationally fixed manner, with each control pulse which it receives at one of its two supply connections 105 and 106, in one or the other direction of rotation, a rotation corresponding to a constant - small - incremental angle of rotation executes such as an angle of 3.6 °, ie that a hundred pulses are necessary for the armature of the electric motor 82 to rotate through 360 °.
  • the electric motor 82 is used in the follow-up control valve 61 for position setpoint specification control, which is achieved by - program-controlled - sequence of the control pulses which are fed to the electric motor 82 at its one supply connection 105 or at its other supply connection 106.
  • a downstream valve 109 which is connected between the control connection 69 leading to the upper drive pressure chamber of the drive cylinder 31 and the reservoir 51 of the pressure supply unit 49, is provided, via which the piston moves rapidly during downward movements 33 of the left drive cylinder 31 - and the upper tool 11 of the bending machine 10 - pressure medium can flow from the reservoir 51 of the pressure supply unit 49 into the upper drive pressure chamber 43.
  • This post-flow valve 109 which is illustrated to illustrate its function as a springless check valve, is of a construction known per se, so realizes that it responds to minimal pressure differences between the upper drive pressure chamber 43 of the drive cylinder 31 and the reservoir 51 of the pressure supply unit 49 and assumes its blocking position when the pressure in the upper drive pressure chamber 43 of the drive cylinder 31 is slightly greater than in the reservoir 51 of the pressure supply unit 49 and changes to its open position as soon as the pressure in the upper drive pressure chamber 43 of the drive cylinder 31 is slightly less than the pressure in the “unpressurized” reservoir 51 of the pressure supply unit, where “unpressurized” is intended to mean equality with the surrounding atmospheric pressure.
  • the outflow valve 111 is designed as a pressure-controlled 2/2-way valve, the basic position 0 of which is its blocking position, into which it is urged by the valve spring 112. Its second functional position I is a flow position, in which the control connection 69 of the drive cylinder 31 via the flow path 13 of the discharge valve 111 in addition to the flow path leading to the reservoir 51 via the throttle orifice 68 and the follow-up control valve 61, which is designated as a whole by 114 the reservoir 151 of the pressure supply unit 49 is connected.
  • the outflow valve 111 has a first, schematically indicated control pressure chamber 116, which is acted upon by the pressure prevailing at the control outlet 66 of the follow-up control valve 61, and a second, likewise schematically indicated, control pressure chamber 117, which is connected to that in the upper drive pressure chamber 43 of the drive cylinder 31 prevailing pressure is applied.
  • the control piston surfaces of the discharge valve 111 provided as a slide valve, which delimit the control pressure spaces 116 and 117, are coordinated with one another in such a way that, assuming the same pressures in the two control pressure spaces 116 and 117, the force resulting from the pressurization of the valve as shown 3 "right" control pressure chamber 117 results and the piston of the outflow valve represented by the circuit symbol 111 tries to urge in its flow position, is equal to the sum of the restoring force of the valve spring 112 and the force resulting from the pressurization of the first control pressure chamber 116, which is "left” as shown in FIG. 3, which urge the piston of the discharge valve 111 into its basic position .
  • a minimal pressure drop across the throttle 68 is sufficient to switch the outflow valve 111 to its flow-through position I in the rapid retraction mode of the piston 33 of the drive cylinder 31.
  • the pressure supply unit 49 is permanently in operation and that the high pressure pump 57 of the pressure supply unit 49 is designed as a regulated pump which only maintains the pressure in the lower drive pressure chambers 46 and 47 of the two drive cylinders 31 and 32 that is required to the pistons 33 and 34 and with them the upper tool 11 in the upper end position hold and in this operating state of the bending machine 10 to compensate for any leakage oil loss that may occur.
  • the overrun control valves 61 and the outflow valves 111 of the electrohydraulic control unit 48 are in the basic positions shown in FIG. 3, whereby the afterflow valves 109 can be open or closed.
  • These post-flow valves 109 are designed so that their valve bodies (not shown in detail) come into the open position due to the installation position of the valves 109 due to the force of gravity acting on them, but with a slight excess pressure in the upper drive pressure spaces 43 and 44 of the two drive cylinders 31 and 32 are "raised” into the locked position.
  • the high-pressure pump 57 of the pressure supply unit 49 is designed with regard to the maximum delivery capacity in such a way that its delivery volume Q, based on the time unit, has only a value which is sufficient for the load feed operation of the drive cylinder 31, in which the feed speed is only 1/10 of the speed Feed rate, in the selected explanatory example thus 30 mms ⁇ 1, to maintain the maximum pressure of 300 bar required for the bending or pressing processing of the workpiece 13 in the upper - large area - drive pressure chamber 43 of the drive cylinder 31.
  • the maximum delivery volume Q of the high-pressure pump 57 is approximately 1 ls ⁇ 1 or 60 l / min, respectively the cross-sectional area of the upper drive pressure chamber 43 or the effective piston surface 52 of the piston 33, which has the value 167 cm2 in order to develop a maximum feed force of 500 kN at a maximum operating pressure of 300 bar.
  • the delivery volume of the high-pressure pump 57 related to the time unit plus the volume of pressure medium related to the time unit, which is displaced in the course of the downward movement of the piston 33 of the drive cylinder 31 from its lower drive pressure chamber 46 and via that in the functional position I of the follow-up control valve 61 open flow path 74 of the same can also flow to the upper drive pressure chamber 43 of the drive cylinder 31, is not sufficient to keep this upper drive pressure chamber 43 completely filled with pressure medium, a slight negative pressure arises in the upper drive pressure chamber 43 in the rapid downward operation of the drive cylinder 31, but it does is sufficient to control the afterflow valve 109 into its open position, so that pressure medium can now flow from the reservoir 51 of the pressure supply unit 49 via the afterflow valve 109 into the upper drive pressure chamber 43 of the drive cylinder 31.
  • the pinion 86 is seen in the direction of the arrow 121 of FIG. 4 via the rack 87 of the feedback device 84, 86, 87 performing this movement driven by the arrow 122 symbolized clockwise, with the result that the hollow shaft 79 - because of the meshing engagement of the spindle thread 84 with the internal thread 83 of the hollow shaft 79 - is again pulled in the direction of the arrow 123 of Figure 4 to the left, so that the flow cross section of the flow path 74 of the follow-up control valve 61 decreases again, but this remains in its functional position I in accordance with the setpoint value, which is controlled by the electric motor 82.
  • the control of the rapid retraction operation of the two drive cylinders 31 and 32 is achieved in an analogous manner in that - in the case of the left drive cylinder 31 - control pulses are fed to the setpoint control motor 82 at its second supply connection 106 - the upward control connection - whereby the electric motor 82 is driven in a counterclockwise direction 107 and the follow-up control valve 61 reaches its functional position II, in which its control output 66 is connected via the flow path 73 of the valve piston 72 to the unpressurized reservoir 51 of the pressure supply unit 49 and the high pressure pump 57 with all of it Delivery volume works in the lower drive pressure chamber 46 of the drive cylinder 31, the piston 33 of which is thereby moved upwards in rapid upward operation.
  • a switch-off element which acts as an "end switch” and is shown as an inductive transmitter 126, is also provided, which emits an electrical signal for switching off upward control pulses for the electric motor 82 when the deflection stroke of the valve actuating element 88 in the direction of the arrow 123 in turn exceeds a threshold value with which an excessive value of the drive pressure is linked in the lower drive pressure chamber 46 of the drive cylinder 31.
  • the occurrence of excessive pressure in the upward operation is an indication in the majority of the statistically significant operating situations that the drive cylinder 31, e.g. due to uneven feed speed of the pistons 33 and 34 of both drive cylinders 31 and 32 "sticks", which is an overall "dangerous" operating situation for the bending machine 10, which must be ended for safety reasons.
  • the rack 87 of the respective mechanical feedback device of the overrun control valve 61 is provided with a compensation cylinder, designated overall by 127, which, with increasing pressure in the upper drive pressure chamber 43 of the drive cylinder 31, is one of the linked thereto vertical expansion of the respective side cheek 17 or 18 of the machine frame 14 corresponding extension of the rack 87 mediated.
  • the compensation cylinder 127 is designed as a single-acting linear cylinder, the housing 128 of which has a Ball joint 129 is connected to the upper tool 11 and carries out its downward and upward movements.
  • a pressure chamber 132 is delimited in the axial-vertical direction by the bottom 129 of the cylinder housing 128 and a piston 131 that can be displaced in a pressure-tight manner.
  • the pressure chamber 132 is connected to the control connection 69 of the upper drive pressure chamber 43 of the drive cylinder 31 via a control line 133 that is flexible at least in sections.
  • the piston 131 is urged into the basic position linked to the minimal volume of the pressure chamber 132 of the compensating cylinder 127 by a prestressed coil spring 134, which is supported on the one hand on the piston 131 and on the other hand on an end end wall 136 of the cylinder housing 128 opposite the bottom 129 of the cylinder housing 128.
  • the toothed rack 87 is designed as a free end section of a piston rod 138 which is firmly connected to the piston 131 and emerges vertically through a central bore 137 in the end end wall 136 of the cylinder housing 128.
  • Bias and spring rate of the coil spring 134 are matched to one another and also adapted to the effective area of the piston 131 of the compensating cylinder 127, that if and for as long as the pressure in the upper drive pressure chamber 43 of the drive cylinder 31 is equal to or approximately the same as that in the reservoir 51 of the pressure supply unit 49 prevailing ambient pressure - atmospheric pressure - is, the connection between the rack 87 and the upper tool 11, seen in the vertical direction, is sufficiently rigid by one to ensure exact feedback of the position of the upper tool 11 in the rapid operating states of the drive cylinder 31 and, on the other hand, to ensure that the displacement of its piston 131 which occurs when the pressure chamber 132 of the compensation cylinder 127 is pressurized corresponds to the amount after the expansion of the side cheeks 17 and 18, which experience this under the development of the feed force of the drive cylinders 31 and 32.
  • the compensation device again designated overall by 127, is structurally and functionally largely identical or analogous to that explained with reference to FIG. 3.
  • the same reference numerals are given in FIG. 5 as in FIG. 3, this is intended to indicate the structural and functional identity or analogy and also the reference to the explanation already given with reference to FIG. 3 of the parts designated in this way include.
  • a lower radial transverse bore 144 of the piston rod 33 opens, to which the connection block 141 is connected in a pressure-tight manner and which has a transverse channel 146 which continues the radial transverse bore of the cylinder piston, via a short longitudinal channel 147 into the pressure chamber 132 of the compensation cylinder 127 opens, so that its pressure chamber 132 is communicatively connected to the upper drive pressure chamber 43 of the drive cylinder 31 via the longitudinal channel 147, the transverse channel 146, the transverse bore 144, the longitudinal bore 142 and the upper transverse bore 143.
  • the follow-up control valve provided in connection with the compensation cylinder 127 according to FIG. 5 has a mechanical feedback element which is connected to the piston 131 of the compensation cylinder 127 is connected non-displaceably, a non-rotatably arranged on the housing 74 'of the follow-up control valve 61' threaded spindle 84 '' which is of sufficient length is so that it can remain in meshing engagement within the entire possible stroke with the internal thread of the hollow shaft 79 coaxially surrounding it of the follow-up control valve 61 ', which is arranged here with its longitudinal axis 78 parallel to the central longitudinal axis 28 of the drive cylinder 31.
  • the driven gear 81 of the electric motor 82 provided for setting the setpoint value is coupled in motion to the drive gear 80 of the hollow shaft 79 via a toothed belt 148.
  • follow-up control valve 61 is structurally identical to that shown in FIG. 4.
  • An inertia-related coupling 139 is further provided, due to the inertia-related further rotation of the setpoint-setting motor 82, which could cause undesired further movement of the pistons 33 and 34 of the drive cylinders 31 and 32, which could be dangerous for an operator in particular in the rapid downward operation of the bending machine which automatically changes into its blocking position mediating the fixing of the rotor of the electric motor 82 in the event of a power failure.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Control Of Presses (AREA)

Abstract

Dans une machine à entraînement hydraulique qui comprend en tant que cylindres d'entraînement deux cylindres différentiels verticaux latéralement espacés sur les jumelles latérales du bâti de la machine, deux soupapes de régulation par poursuite fonctionnant sur la base d'une indication mécanique de la valeur réelle de la position, ainsi que de l'attribution par commande électrique d'une valeur de consigne de la position d'un outil supérieur, servent d'éléments de commande. Les soupapes de régulation ont une position de base de blocage et deux positions alternatives de passage correspondant à l'avance rapide et en charge, vers le bas, en direction de la pièce à usiner, et au retour en arrière par rapport à la pièce à usiner. Les pistons des cylindres d'entraînement délimitent avec une surface de piston une chambre supérieure de compression d'entraînement et avec une surface plus petite de piston une chambre inférieure de compression d'entraînement des cylindres d'entraînement, ces chambres étant traversées axialement par la tige correspondante de piston avec laquelle l'outil supérieur est relié. Dans le mode de fonctionnement à avance rapide, le poids de l'outil supérieur et du piston sont utilisés comme force d'entraînement et du milieu sous pression s'écoule à travers des soupapes d'apport dans les chambres supérieures de compression d'entraînement. Dans le mode de fonctionnement à avance en charge, une pression élevée s'exerce dans les chambres supérieures de compression d'entraînement. Pendant le retour en arrière, la pression dans les chambres supérieures de compression d'entraînement est déchargée à travers des soupapes d'écoulement commandées par pression.

Claims (16)

  1. Machine à entraînement hydraulique pour l'usinage par façonnage à froid, en particulier par cintrage ou matriçage, d'une pièce en tôle placée entre un outil inférieur (12) et un outil supérieur (11) lequel peut être déplacé verticalement vers le haut et vers le bas en face dudit outil inférieur et pour l'entraînement duquel sont prévus deux cylindres d'entraînement (31, 32) disposés à distance latérale l'un de l'autre et conformés en cylindres différentiels dont les pistons (33, 34) comportent des tiges de piston (38, 39) lesquelles sortent par le bas des corps de cylindre (36, 37) et auxquelles l'outil supérieur (11) est relié, pour la compensation de légères différences de course des pistons (33, 34), par des articulations uniaxes dont les axes d'articulation s'étendent perpendiculairement par rapport au plan marqué par les axes centraux des cylindres d'entraînement, le rapport F₁/F₂ des surfaces F₁ et F₂ des pistons par lesquelles ceux-ci séparent à chaque fois une chambre de compression d'entraînement supérieure (43, 44) d'une chambre de compression d'entraînement inférieure (46, 47) traversée axialement par la tige de piston dont l'alimentation simultanée ou alternative en pression et/ou la décompression - commandées par des soupapes - permettent de commander des mouvements d'avance rapide et des mouvements d'avance en charge dirigés vers la pièce à usiner (13) ainsi que des mouvements de retour rapide dans la direction opposée à la pièce à usiner, étant compris entre 5 et 20, lors du mouvement d'avance rapide, la chambre de compression d'entraînement supérieure (43, 44) délimitée par une surface plus grande communiquant avec le réservoir (51) sans pression du groupe d'alimentation en pression par l'intermédiaire d'une vanne d'écoulement (109), et la chambre de compression d'entraînement inférieure (46, 47) étant reliée, par l'intermédiaire d'un élément de commande (48) à effet d'étranglement réglable, à la chambre de compression d'entraînement supérieure (43, 44) du cylindre d'entraînement (31, 32) respectif, lors du mouvement d'avance en charge, les chambres de compression d'entraînement inférieure et supérieure étant alimentées ensemble en pression, et lors du mouvement de retour rapide, la chambre de compression d'entraînement inférieure (46, 47) étant soumise à une forte pression, tandis que la chambre de compression d'entraînement supérieure est décompressée, et pour la commande des mouvements des pistons et de leur synchronisme étant prévue une unité de commande électrohydraulique (48) opérant par prédétermination de la valeur de consigne de position à commande électrique et comparant la position effective des pistons (33,34) et respectivement de l'outil supérieur (11) couplé avec ceux-ci, avec la valeur de consigne, caractérisée en ce que, dans le cadre de l'unité de commande électrohydraulique (48), elle comprend respectivement, comme éléments de commande associés aux deux cylindres d'entraînement (31 et 32), une vanne-pilote d'asservissement (61) pour chacun des cylindres (31 et 32) fonctionnant avec une répétition mécanique de la valeur effective de la position du piston respectif (33 ou 34), conformée en vanne proportionnelle, et pouvant être utilisée comme vanne à 3/3 voies, avec une position de blocage (0) dans laquelle la sortie de commande (66) de ladite vanne-pilote d'asservissement (61) reliée au raccord de commande (69) de la chambre de compression d'entraînement supérieure (43) du cylindre d'entraînement associé (31 et respectivement 32) est bloquée aussi bien par rapport à la sortie haute pression (62) du groupe d'alimentation en pression (49) que par rapport au réservoir (51) de celui-ci, avec une première position de passage (I) associée au régime d'avance rapide aussi bien que d'avance en charge du cylindre d'entraînement respectif (31 ou 32) dans laquelle le raccord d'alimentation P (63) relié à la sortie haute pression (62) du groupe d'alimentation en pression (49) communique avec la sortie de commande (66) de la vanne-pilote d'asservissement (61) et dans laquelle celle-ci est bloquée par rapport au raccord d'alimentation T (64) de la vanne-pilote d'asservissement (61) qui communique avec le réservoir (51) sans pression du groupe d'alimentation en pression (49), ainsi qu'avec une seconde position de passage (II) associée au régime de retour rapide du cylindre d'entraînement respectif (31 ou 32) dans laquelle le raccord de commande (69) de la chambre de compression d'entraînement supérieure (43) du cylindre d'entraînement respectif (31 ou 32) communique avec le réservoir (51) et est bloqué par rapport à la sortie haute pression (62) du groupe d'alimentation en pression (49), que la sortie haute pression (62) du groupe d'alimentation en pression (49) est raccordée en permanence à la chambre de compression d'entraînement inférieure (46) du cylindre d'entraînement respectif (31 ou 32), et que hydrauliquement en parallèle avec la vanne d'écoulement (109) est prévue une vanne à 2/2 voies conformée en vanne d'écoulement (111) qui, au cours des phases de mouvement de retour rapide du piston (33 et respectivement 34) du cylindre d'entraînement respectif (31 ou 32), peut être amenée dans sa position de fonctionnement I dans laquelle est établie une liaison directe entre ladite vanne d'écoulement et le réservoir (51) et qui occupe par ailleurs sa position de base 0 - position de blocage.
  2. Machine selon la revendication 1, caractérisée en ce que le débit maximum de la pompe haute pression (57) du groupe d'alimentation en pression (49), rapporté à l'unité de temps, est au moins approximativement égal à la quantité de fluide sous pression qui doit être refoulée dans la chambre de compression d'entraînement supérieure (43) du cylindre d'entraînement respectif (31 ou 32) pour que le piston (33 et respectivement 34) dudit cylindre d'entraînement (31 et respectivement 32) effectue son mouvement d'avance en charge à la vitesse d'avancement appropriée.
  3. Machine selon la revendication 2, caractérisée en ce que la pompe haute pression (57) du groupe d'alimentation en pression (49) est réalisée sous la forme d'une pompe commandée par pression dont le refoulement est inversement proportionnel à la pression de sortie produite à sa sortie.
  4. Machine selon l'une des revendications 2 ou 3, caractérisée en ce qu'elle comprend un limiteur de pression (59) avec valeur de seuil de réponse réglable pour la pression, qui est monté en parallèle avec la pompe haute pression (57) du groupe d'alimentation en pression (49).
  5. Machine selon l'une des revendications 1 à 4, caractérisée en ce que la vanne d'écoulement (111) est conformée en électrovanne qui, à partir d'une fréquence minimale, est amenée dans sa position de passage I par des impulsions électriques de prédétermination de la valeur de consigne de position générées pour la commande des mouvements de retour rapide des pistons (33 et 34) des cylindres d'entraînement et permettant de commander un moteur électrique (82) prévu pour la commande de la prédétermination de la valeur de consigne de la vanne-pilote d'asservissement (61).
  6. Machine selon l'une des revendications 1 à 4, caractérisée en ce que la vanne d'écoulement (111) est réalisée sous la forme d'une vanne commandée par pression qui est amenée, par alimentation en pression d'une première chambre de compression de commande (116), dans sa position de base (0) - position de blocage - et, par alimentation en pression d'une seconde chambre de compression de commande (117), dans sa position de passage I, que la première chambre de compression de commande (116) est raccordée à la sortie de commande (66) de la vanne-pilote d'asservissement (61) et la seconde chambre de compression de commande, au raccord de commande (69) de la chambre de compression d'entraînement supérieure (43) du cylindre d'entraînement (31 et respectivement 32), qu'entre celles-ci et la sortie de commande (66) de la vanne-pilote d'asservissement (61) est intercalé un étranglement (68) et, en parallèle avec celui-ci, un clapet antiretour (67) qui est maintenu dans sa position de fermeture lorsque la pression est plus élevée dans la chambre de compression d'entraînement supérieure (43) qu'à la sortie de commande (66) de la vanne-pilote d'asservissement (61), et que la surface du piston de commande pouvant être sollicitée par la pression régnant à la sortie de commande (66) de la vanne-pilote d'asservissement (61) et délimitant de manière mobile la seconde chambre de compression de commande (117) de la vanne d'écoulement (111) correspond au moins et est approximativement égale à la surface du piston de commande délimitant de manière mobile la première chambre de compression de commande et sollicitée par la pression régnant dans la chambre de compression d'entraînement supérieure (43) du cylindre d'entraînement (31 et respectivement 32), et qu'il est prévu un ressort à soupape (112) qui pousse la vanne d'écoulement (111) dans sa position de base (0) - position de blocage - et dont la force de rappel équivaut à une petite fraction de par exemple 1/20 à 1/5 d'une chute de pression se produisant sur l'étranglement (66).
  7. Machine selon la revendication 6, caractérisée en ce que les surfaces des pistons de commande de la vanne d'écoulement (111) pouvant être sollicitées par la pression de commande, et la précontrainte du ressort à soupape (112) sont accordées mutuellement en ce sens que la vanne d'écoulement (111) est commutée dans sa position de passage I dès que la chute de pression se produisant sur l'étranglement (68) dépasse une valeur de 1 bar.
  8. Machine selon l'une des revendications 1 à 7, caractérisée en ce que le dispositif de répétition de la valeur de position effective (86, 87) de la vanne-pilote d'asservissement (61) comprend un dispositif de compensation (127) qui provoque un relèvement de la position de référence correspondant à la valeur d'un élargissement vertical du bâti de machine (14, 23, 24) que celui-ci subit sous l'effet des forces d'avancement appliquées au moins en régime d'avance en charge, à laquelle est rapportée la répétition de position.
  9. Machine selon la revendication 8, dans laquelle le dispositif de répétition de la valeur de position effective comprend un pignon couplé de manière solidaire en rotation avec une broche de répétition de la vanne-pilote d'asservissement, et une crémaillère coopérant avec celui-ci ou une broche filetée (84'') coopérant avec un écrou de broche en forme d'arbre creux dont les rotateurs motorisés assurent la prédétermination de la valeur de consigne de position, ladite broche filetée suivant les mouvements du piston du cylindre d'entraînement respectif et s'étendant parallèlement à l'axe longitudinal de celui-ci, caractérisée en ce que la crémaillère (87) et respectivement la broche filetée du dispositif de répétition mécanique (86, 87) de la vanne-pilote d'asservissement (61) est munie d'un cylindre de compensation (127) qui, au fur et à mesure que la pression dans la chambre de compression d'entraînement supérieure (43) du cylindre d'entraînement respectif (31 ou 32) augmente, assure un allongement correspondant de la crémaillère (87) et respectivement de la broche filetée (84'') en fonction de l'élargissement vertical des faces latérales (17 et 18) du bâti de machine (14).
  10. Machine selon la revendication 9, caractérisée en ce que le cylindre de compensation (127) est conformé en cylindre hydraulique linéaire à simple effet dont le corps (128) est solidarisé en translation avec la tige de piston (33 et respectivement 34) du cylindre d'entraînement respectif (31 et respectivement 32) ou, à proximité immédiate de l'axe respectif (28 ou 29) des cylindres, avec l'outil supérieur (11), le fond (129) du corps de cylindre (128) et un piston (131) déplaçable dans celui-ci de manière étanche délimitant de façon mobile dans le sens axial-vertical, une chambre de compression (132) qui est maintenue en communication avec la chambre de compression d'entraînement supérieure (43) du cylindre d'entraînement respectif (31 ou 32), que le piston (131) est poussé dans la position de base correspondant au volume minimum de la chambre de compression (132) du cylindre de compensation (127) par un ressort de rappel (134) précontraint qui s'appuie d'une part sur le piston (131) et d'autre part sur une paroi frontale d'extrémité (136) du corps de cylindre (128) disposée en face du fond (129) dudit corps de cylindre (128), et que la crémaillère (87) et respectivement la broche filetée (84'') est conformée en section terminale libre d'une tige de piston (138) qui est solidaire du piston (131) et sort verticalement du corps de cylindre (128), la précontrainte et la course élastique du ressort hélicoïdal (134) ainsi que la surface active du piston (131) du cylindre de compensation (127) étant adaptées mutuellement de telle façon que, lors d'une alimentation en pression de la chambre de compression (132) du cylindre de compensation (127), le déplacement de son piston (131) correspond à la valeur de l'élargissement des faces latérales (17 et 18) que celles-ci subissent sous l'effet de la force d'avancement développée par les cylindres d'entraînement (31 et 32)
  11. Machine selon la revendication 10, caractérisée en ce que la chambre de compression (132) du cylindre de compensation (127) est reliée par une conduite de commande (133) flexible au moins par sections, au raccord de commande (69) de la chambre de compression d'entraînement supérieure (43) du cylindre d'entraînement respectif (31 ou 32).
  12. Machine selon la revendication 10, caractérisée en ce que le corps (128) du cylindre de compensation (127) est solidarisé avec la tige de piston (33 et respectivement 34) du cylindre d'entraînement respectif (31 ou 32) par l'intermédiaire d'un élément de raccordement en forme de bloc muni d'un alésage de conduction qui communique d'une part avec un alésage de conduction qui traverse axialement le piston (33 et respectivement 34) et débouche dans la chambre de compression d'entraînement supérieure (43) de celui-ci et, d'autre part, avec la chambre de compression (132) du cylindre de compensation (127).
  13. Machine selon l'une des revendications 1 à 12, caractérisée en ce que la vanne-pilote d'asservissement (61) est équipée d'un système de capteurs (124, 126) qui, pour l'utilisation comme signaux d'avertissement et/ou comme signaux de commande par lesquels la machine (10) peut être mise à l'arrêt, génère des signaux électriques de sortie si la course de déviation du corps (72) de la vanne-pilote d'asservissement (61) dans la position de fonctionnement associée au régime d'avancement des cylindres d'entraînement (31 et 32) ou au régime de retour, dépasse une valeur de seuil prédéterminée.
  14. Machine selon la revendication 13, caractérisée en ce que les signaux de sortie générés par les capteurs (124, 126) du système de capteurs sont, en niveau et/ou en fréquence, un critère pour la valeur de la déviation du corps (72) de la vanne-pilote d'asservissement (61) dans les positions de fonctionnement (I et II) de celle-ci.
  15. Machine selon la revendication 14, caractérisée en ce qu'au moins en régime d'avance rapide ainsi qu'en régime de retour rapide des cylindres d'entraînement (31 et 32), la fréquence de sortie des impulsions de prédétermination de la valeur de consigne de position baisse progressivement au fur et à mesure de l'augmentation de la course de déviation du corps (72) de la vanne-pilote d'asservissement (61).
  16. Machine selon l'une des revendications 1 à 15, caractérisée en ce que le moteur électrique (82) prévu pour la commande de la prédétermination de la valeur de consigne de position comporte un accouplement (139) débrayable par activation électrique ou un frein qui, en cas de défaillance de l'alimentation électrique ou lors d'une interruption de la commande électrique de la position de désaccouplement, passe automatiquement à une position de blocage dans laquelle est réalisée l'immobilisation du rotor du moteur électrique (82).
EP91915910A 1990-11-28 1991-09-13 Machine a entrainement hydraulique avec deux cylindres d'entrainement Expired - Lifetime EP0559651B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT9191915910T ATE105529T1 (de) 1990-11-28 1991-09-13 Hydraulisch angetriebene maschine mit zwei antriebszylindern.

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4037848 1990-11-28
DE4037848A DE4037848A1 (de) 1990-11-28 1990-11-28 Hydraulisch angetriebene maschine mit zwei antriebszylindern
PCT/EP1991/001742 WO1992009425A1 (fr) 1990-11-28 1991-09-13 Machine a entrainement hydraulique avec deux cylindres d'entrainement

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EP0559651A1 EP0559651A1 (fr) 1993-09-15
EP0559651B1 true EP0559651B1 (fr) 1994-05-11

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DE4412224A1 (de) * 1994-04-09 1995-10-12 Graebener Pressensysteme Gmbh Presse für eine Kaltverformung von Metallwerkstücken
WO1999054123A1 (fr) * 1998-04-07 1999-10-28 Mannesmann Rexroth Ag Procede de fonctionnement d'une presse hydraulique
RU2351450C1 (ru) * 2007-07-11 2009-04-10 Ярославский государственный технический университет Устройство контроля процесса запрессовки при получении прессового соединения объектов цилиндрической формы
CN113415026B (zh) * 2021-06-23 2022-02-25 南京恒久机器制造有限公司 一种远程监控式油电混合电液伺服折弯机智能控制系统及其方法
CN116336247B (zh) * 2023-05-25 2023-07-25 中国航空工业集团公司沈阳空气动力研究所 具备双向保护功能的暂冲式风洞调压阀控制装置及方法

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US2211692A (en) * 1936-08-03 1940-08-13 Oilgear Co Hold-down system
US4148203A (en) * 1977-10-07 1979-04-10 Dreis & Krump Mfg. Co. Computer-controlled press brake
FR2509222A1 (fr) * 1980-06-11 1983-01-14 Ettore Alagna Presse plieuse hydraulique avec systeme de compensation des deformations elastiques
DE3609632A1 (de) * 1986-03-21 1987-09-24 Fritz Hakemann Abkantpresse zum gesenkbiegen von insbesondere blechen

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WO1992009425A1 (fr) 1992-06-11
EP0559651A1 (fr) 1993-09-15
DE4037848A1 (de) 1992-06-04
DE59101620D1 (de) 1994-06-16

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