EP0339247B1 - Hydraulische Steuereinrichtung für die Antriebssteuerung eines doppelt-wirkenden Hydrozylinders - Google Patents

Hydraulische Steuereinrichtung für die Antriebssteuerung eines doppelt-wirkenden Hydrozylinders Download PDF

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Publication number
EP0339247B1
EP0339247B1 EP89104861A EP89104861A EP0339247B1 EP 0339247 B1 EP0339247 B1 EP 0339247B1 EP 89104861 A EP89104861 A EP 89104861A EP 89104861 A EP89104861 A EP 89104861A EP 0339247 B1 EP0339247 B1 EP 0339247B1
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EP
European Patent Office
Prior art keywords
pressure
valve
hydraulic cylinder
piston
operating
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP89104861A
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German (de)
English (en)
French (fr)
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EP0339247A1 (de
Inventor
Eckehart Schulze
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Schulze Eckehart
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Schulze Eckehart
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Priority to AT89104861T priority Critical patent/ATE92804T1/de
Publication of EP0339247A1 publication Critical patent/EP0339247A1/de
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D28/00—Shaping by press-cutting; Perforating
    • B21D28/002—Drive of the tools
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J9/00—Forging presses
    • B21J9/10—Drives for forging presses
    • B21J9/20—Control devices specially adapted to forging presses not restricted to one of the preceding subgroups
    • 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
    • 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
    • B30B15/161—Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high pressure

Definitions

  • the invention relates to a hydraulic control device for the drive control of a double-acting hydraulic cylinder, which is provided as a drive element for the tool of a processing machine, with which a workpiece can be subjected to a punching or a shaping cold deformation, and with the others, in the preamble of patent claim 1 mentioned generic features.
  • Such a known control device is in connection with a hydraulic drive device, in which a linear hydraulic cylinder designed as a differential cylinder is provided as the drive element, in which the area ratio F A / F G of its larger drive area F A and its smaller drive or counter surface F G is about 1/3, described in DE 37 35 123 A1.
  • the surface switch valve is controlled by the pressure in the smaller drive pressure chamber of the hydraulic cylinder as soon as this pressure exceeds a threshold value of a predetermined amount is lower than the maximum value of the output pressure of the pressure supply unit, switched to its position assigned to the load feed operation, in which the smaller drive pressure chamber of the hydraulic cylinder is now depressurized and only the larger drive pressure chamber via the directional and movement control valve is connected to the pressure outlet of the pressure supply unit, at which a high pressure with a typical value of 200 bar is provided.
  • the surface switching valve when the need for feed force is only slightly greater than the force that can be reached in differential operation, does not simply switch back and forth repeatedly, which in unfavorable cases not only delays the work process, but even could lead to the piston "stopping", the surface switch valve is designed so that it only switches back to differential operation after the need for feed force has become lower by a predetermined safety margin than that in differential operation of the Hydraulic cylinder maximum achievable feed force.
  • the hydraulic actuating device according to the older patent application DE-A-37 35 123.0 works satisfactorily insofar as in numerous cases in which the feed force which can be achieved in the differential operation of the hydraulic cylinder is approximately sufficient and only in rare cases has to be switched over to the operation with one-sided pressurization of the hydraulic cylinder piston , favorable short cycle times can be achieved.
  • the area ratio of the hydraulic cylinder must be chosen to be relatively large, but this has the consequence that when the surface switching valve has responded, a correspondingly large increase in the feed force which can now be achieved is achieved, which, even while the tool is being pierced, can already lead to considerable acceleration of the hydraulic cylinder piston, which can then be achieved by switching the surface switching valve back in Whose function position assigned to the differential operation of the hydraulic cylinder has to be caught again, which can lead to considerable impacts, the more the "easier” the tool could pierce the workpiece and accordingly a "runaway" of the drive cylinder can occur before the intercepted by switching back to differential operation.
  • the object of the invention is therefore to improve a control device of the type mentioned in such a way that its use in combination with a simple differential cylinder as the drive element of a hydraulic drive device with a simple overall structure, low-vibration operation of the same can be achieved, if necessary, even if with the machine equipped with the drive must be operated with a fast work cycle sequence.
  • the "interception" of the drive cylinder piston in the last phase of the machining of the workpiece only occurs when the pressure supply is switched back to the low pressure level P N , which also facilitates this interception.
  • the control device according to the older patent application depending on the application, can be equipped with a follow-up control valve as a directional control valve, be it for reasons of simple controllability of the movement sequence when using a CNC control, this results
  • the pressure supply unit must be designed for two output pressure levels and a pressure changeover valve arrangement must be present in order to be able to use these different output pressure levels as required.
  • the pressure changeover valve arrangement can be realized by means of a simple check valve, which, as it were, mediates the decoupling of the pressure outputs of the pressure supply unit and by means of a simple pressure-controlled 2/2-way valve the features of claim 3 a typical design and configuration is given as a slide valve, which can be equipped with a return spring adjustable bias to adjust the restoring force and adaptation to the desired switching threshold.
  • the lower outlet pressure of the pressure supply unit can be used in a simple manner to generate the restoring force that is required for setting the changeover threshold.
  • the preferred design of the pressure changeover valve according to claim 5 has the advantage that no resilient resetting elements are required to set the pressure changeover valve to the required pressure changeover threshold. There is also at least one wear part that is otherwise exposed to considerable loads.
  • the features of claim 6, on the one hand, provide a structurally simple design of the surface changeover valve and dimensioning regulations for the design of control surfaces of a control valve piston and the clear cross-sectional area of the valve channel of a seat valve of the surface changeover valve, when observed, a high reliability of the function Control is achieved.
  • claims 7 to 11 indicate special designs and dimensions of the pressure changeover valve and the surface changeover valve, the drive hydraulic cylinder and the pressure supply unit, which have proven to be particularly advantageous in combination with the control device according to the invention.
  • the purpose of the hydraulic control device according to the invention shown in FIG. 1, to the details of which is expressly referred to, designated overall by 10, is the need-based pressurization and / or relief of the drive pressure chambers 11 and / or 12 of a double-action system, designated overall by 13 , linear hydraulic cylinder, which in a punching or embossing machine, more generally a processing machine, by means of which a workpiece 14, for example a steel plate, can be subjected to a piercing - punching - or a shaping cold deformation, as a drive element for the tool 16 thereof Machine is provided which, in the course of a working cycle of this machine, executes a rapid feed movement toward the workpiece 14, through which the tool 16 comes into contact with the workpiece 14, thereafter - if necessary, increasing the force acting in the feed direction and reducing the Advance b-speed executes its load feed movement, which mediates the machining of the workpiece 14, and then, after the workpiece 14 has undergone its desired deformation, is brought back again
  • the hydraulic cylinder 13 is, without restriction of generality, provided as "standing”, i.e. with a vertical course of its central longitudinal axis 17 with respect to a horizontally arranged machine table 18, by which a machine frame, not otherwise shown, is to be represented, on which, fixed to the frame, the housing 19 of the hydraulic cylinder 13 is also permanently mounted.
  • the workpiece 14 resting on the machine table 18 can be fixed to the machine table 18 by means of a holding device (not shown) or relative to it, according to a "processing path", e.g. be numerically controlled, movable.
  • the hydraulic cylinder 13 is designed as a differential cylinder, the piston, which is designated as 21 and can be displaced up and down within the cylinder housing 19 within the cylinder bore 22, delimits the two drive pressure spaces 11 and 12 in a pressure-tight manner by means of their valve-controlled, common or alternative action the outlet pressure P N or P H of a pressure supply unit designated overall by 23 and, if necessary, pressure relief of each of the two drive pressure chambers 11 or 12, the feed and retraction strokes of the piston 21 or of the tool 16 required for machining the workpiece 14 can be controlled as required in the above sense.
  • the pressure supply unit 23 has a first supply pressure outlet 24, at which a relatively low supply pressure P N is provided, which has a typical value of 60 bar, and a second supply pressure outlet 26, at which a significantly higher pressure P H is provided which has a typical value of 180 bar.
  • the pressure supply unit 23 based on its special design because it can be assumed to be known, is regarded as sufficiently explained by this — for example — design.
  • P G (2) where P G denotes the pressure which results as a function of the effective load counterforce and the operating pressure P A coupled into the larger drive pressure chamber 14 in the lower, smaller drive pressure chamber 12, and with F2 the effective cross-sectional area of the cylinder bore 22, in which the cylinder piston 21 with its larger piston stage 31 of the surface F 1 is guided so as to be pressure-tight, by means of an inner housing stage 32 offset - narrower - bore stage 33 of the housing 19, in which the one with the larger piston stage 31 firmly connected, for example in one piece executed, smaller, rod-shaped piston stage 34 is slidably guided pressure-tight, at the lower, free end of the tool 16 is attached.
  • control device 10 provided for the drive control of the hydraulic cylinder 13 is explained in terms of construction and circuit technology with reference to its functional components, the essential functions of the control device 10 are discussed in advance:
  • the hydraulic cylinder 13 In the rapid feed, in which the tool 16 experiences its feed movement toward the workpiece 14, which is directed downward according to FIG. 1, the hydraulic cylinder 13 is operated in differential mode, the pressure supply initially taking place via the low-pressure outlet 24 of the pressure supply unit 23 .
  • the pressure that can be built up in this operation of the hydraulic cylinder 13 in its drive pressure chambers 11 and 12 is sufficient in cases in which the workpiece 14 has a relatively small thickness in order to generate the force required for the deformation of the workpiece 14, so that this, as it were "Rapid feed operation" can be edited.
  • the control device 10 transmits a switchover by responding to a pressure changeover valve 39
  • a pressure changeover valve 39 Operating pressure supply of the hydraulic cylinder 13 to the high-pressure outlet 26 of the pressure supply unit 23, at which a pressure P H can be provided in the typical design thereof, the maximum amount (approx. 180 bar) is significantly higher, for the exemplary embodiment it is assumed 3 times higher than the output pressure P N which can be provided at the low pressure outlet 24 of the pressure supply unit 23 and which may be around 60 bar.
  • the maximum usable feed force with which the tool 16 is driven is given by the relationship (4).
  • the feed speed is reduced compared to the rapid feed operation by the ratio F2 / F1 of the effective areas F2 and F1 of the smaller piston stage 34 and the larger piston stage 31 of the hydraulic cylinder piston 21.
  • the hydraulic cylinder 13 is switched to rapid retraction mode, in which the smaller drive pressure chamber 12, which is designed as an annular space, is connected only to the low-pressure outlet 24 of the pressure supply unit 23 and the larger drive pressure chamber 11 to the pressureless tank 43 of the pressure supply unit 23 is relieved of pressure.
  • Such follow-up control valves are, according to their basic structure, designed as 4/3-way valves, which, however, can also be used as 3/3-way valves with the hydraulic circuit periphery of the hydraulic cylinder 13 shown in FIG. 1 .
  • the pressure changeover valve 39 is designed as a pressure-controlled 2/2-way valve, which has the function as soon as the operating pressure P A in the larger drive pressure chamber 11 of the hydraulic cylinder 13 exceeds a threshold value P A1 , which, for the purpose of explanation, is 90% of the - lower - supply pressure P N provided at the low pressure outlet 24 of the pressure supply unit 23 is assumed, reached or exceeded, is switched from its previously assumed blocking position 0 to a flow position I in which the high pressure outlet 26 of the pressure supply unit 23 is now connected to the supply pressure (P) connection of the follow-up control valve 44 is connected.
  • a check valve 58 is connected, which is held in its blocking position by higher pressure at the supply pressure connection 57 than at the low pressure outlet 24 of the pressure supply unit.
  • the operating pressure P N provided at the low pressure outlet 24 of the pressure supply unit 23 is transmitted to the supply pressure connection 57 of the follow-up control valve 44 while the pressure changeover valve 39 is in its blocking position.
  • the check valve 58 prevents pressure from being coupled over from the high-pressure outlet 26 of the pressure-supply unit 23 to its low-pressure outlet 24.
  • the pressure changeover valve 39 is designed in the special embodiment shown as a slide valve, in the housing 60 of which two bore stages 59 and 61 of different diameters are introduced, which, merging into one another, are offset from one another by an inner, radial housing stage 62 and each have an end end wall 63 or 64 of the housing are completed.
  • the piston which is designated overall by 66, is displaceably guided with an end flange 67 and 68, respectively, in the smaller bore step 59 in diameter or in the larger bore step 61 in diameter, these end flanges 67 and 68 being movable in a pressure-tight manner Form boundaries each of a control pressure chamber 69 and 71, which are closed by the end end walls 63 and 64 fixed to the housing.
  • the control pressure chamber 69 of the pressure changeover valve 39 which is smaller in diameter, is - permanently - connected to the low pressure outlet 24 of the pressure supply unit 23.
  • the control pressure chamber 71 of the pressure changeover valve 39 which is larger in diameter, is connected to the working connection 72 of the follow-up control valve 44 which is connected to the larger drive pressure chamber 11 of the hydraulic cylinder 13.
  • the diameter of the larger end flange 68 is followed by a piston stage 73 corresponding to the diameter of that of the smaller bore 59 of the valve housing 58, by means of which the valve slide 66 is also shown in FIG which is guided so that it is displaceable in a pressure-tight manner according to the smaller housing bore 59.
  • This piston stage 73 is fixedly connected by means of a rod-shaped piston intermediate piece 74 to the end flange 67 of the valve piston 66 which also corresponds to the diameter of the smaller bore step 59, the piston 66 being embodied in one piece overall.
  • the end flanges 67 and 68 each have short support projections 77 and 78, pointing towards the end end walls 63 and 64 of the valve housing 58, in the direction of the central longitudinal axis 76 of the pressure changeover valve 39, by means of which the piston 66 in its functional positions O and I corresponding positions either on the one, according to FIG. 1 "lower” end wall 64 or on the other, according to FIG. 1 "upper" end wall 63 of the valve housing 58 is supported centrally.
  • the valve piston 66 is therefore pushed into its basic position - shown in solid lines - linked to the minimal volume of its larger control pressure chamber 71, if and as long as the - larger - control pressure chamber 71 is coupled into the larger drive pressure chamber 11 of the hydraulic cylinder 13 and at the same time prevailing operating pressure P A is smaller than the value P N divided by the value 1.1 of the low-pressure outlet 24 of the pressure supply unit 23 Provided - lower - supply pressure P N , which is permanently coupled into the smaller control pressure chamber 69 of the pressure changeover valve 39, that is, if: P A ⁇ P N / 1.1 (6) As long as the valve piston 66 assumes
  • the inlet pressure chamber 79 of the pressure changeover valve 39 is - seen in the basic position of the valve piston 66 shown in solid lines - fixed to the housing through the smaller bore step 59 of the valve housing 58 and - axially - movable through the mutually facing, annular, inner end faces 82 and 83 of the smaller end flange 67 of the valve piston 66 and the piston stage 73 adjoining its larger end flange 68.
  • the outlet pressure chamber 81 of the pressure changeover valve 39 is fixed to the housing in the axial direction and radially on the outside by an annular groove 84 made in the smaller bore 59 of the valve housing 58 and radially on the inside by the cylindrical outer surface 86 of the smaller end flange 67 of the valve piston 66.
  • the surface switch valve 42 which is designed as a pressure-controlled 3/2-way valve, provides pressure relief for the smaller one , annular drive pressure chamber 12, with the result that now the entire cross-sectional area F1 of the larger piston stage 31 is used for the feed force development and this thus in cases of high load - large workpiece thickness - down to the value F1.
  • P H can be increased.
  • the still usable feed rate is then reduced by the area ratio F / F 1.
  • this surface switching valve 42 fulfills the function that after it had been switched into its functional position which mediated the pressure relief of the annular drive pressure chamber 12 of the hydraulic cylinder 13 and thereby enabled the use of an increased feed force, only then again in its pressurization of the Annular drive pressure chamber 12 mediating functional position is switched back after the - for example penetrating - machining of workpiece 12 the need for feed force on tool 16 has become a defined minimum amount ⁇ K lower than the amount of feed force or operating pressure in drive pressure chambers 11 and 12 of the hydraulic cylinder 13, by exceeding which the switching of the surface switching valve 42 in which the pressure relief of the annular drive pressure chamber 12 was triggered position.
  • this ensures that, as long as possible, the highest possible feed rate of the tool 16 remains usable and, on the other hand, it ensures that after the control device 10 has switched over in the sense of increasing the feed force, it is not “too early” again to a reduced feed force. is switched back ", which could lead to undesired vibrations and, as a result, to a" standstill "of the tool 16.
  • FIGS. 2 and 3 show two possible operating positions of the surface switching valve 42, while the Surface changeover valve is shown in FIG. 1 in its basic position corresponding to the non-activated state of the drive device.
  • the area changeover valve 42 comprises a first valve chamber 88, which is permanently connected to the tank 43 of the pressure supply unit 23 via a relief flow path 89 and is therefore kept depressurized.
  • This valve chamber 88 is sealed off to the outside by a set screw 91, which forms the end end wall of the valve housing, which is designated as a whole by 90.
  • a valve closing spring 92 is adjustable, which engages a centering piece 93, which urges a valve body formed as a ball 94 of a seat valve, generally designated 96, against its valve seat 97, ie into the closed position of this seat valve 96, which is formed by the inner, ie the clear diameter towards the smaller, edge of a conical depression 98, which in turn serves to center the valve ball 94, of an intermediate wall 99 of the valve housing 90.
  • the central valve chamber 101 is in constant communication with the annular, smaller drive pressure chamber 12 of the hydraulic cylinder 13 via a first hydraulic control line 103.
  • the central valve chamber 101 is bounded by the one, the diameter smaller bore step 104 of a stepped bore of the housing 90, generally designated 106, whose diameter larger bore step 107 at the other end of the housing 90 is sealed pressure-tight by a housing cover 108 forming the end wall of the valve housing 90 there is.
  • a stage piston In the two bore stages 104 and 107 of the stage bore 106, a stage piston, designated overall by 112, is displaceably guided in a pressure-tight manner, each with a piston stage 109 or 111, the smaller piston stage 109 of which forms an axially movable boundary of the central valve chamber 101, and its diameter after larger piston stage 111 on the one hand forms the axially movable boundary of an annular chamber 115 which is axially fixed to the housing by the annular housing stage 113 which mediates between the smaller bore step 104 and the larger bore stage 107, and further forms the axially movable boundary of a control chamber 114, the axial limit of which is fixed to the housing is formed by the housing cover 108.
  • This control chamber 114 is kept in constant communication with the larger drive pressure chamber 11 of the drive hydraulic cylinder via a second hydraulic control line 116.
  • the stepped piston 112 is urged toward the valve ball 94 by a - slightly preloaded - return spring 117, which is supported on the inside of the housing cover 108, on which it rests in the basic position shown in FIG. 1 with a plunger-shaped, axial extension 118 supports its smaller piston stage 109.
  • the outer diameter of this tappet-shaped extension 118 is significantly smaller than the diameter of the valve channel 102 through which it passes.
  • the smaller piston stage 109 is offset from the larger piston stage 111 by an annular groove-shaped constriction 119, which is penetrated by a transverse bore 121 opening into the annular chamber 115.
  • This transverse bore 121 is in constant communication with the central valve chamber 101 via a central longitudinal bore 122 which penetrates the smaller piston stage 109 and its plunger-shaped extension 108 in the axial direction and one or more transverse bore (s) 123 in the plunger-shaped extension 118.
  • the smaller bore step 104 viewed in the direction of the central longitudinal axis 100 of the housing 90, is provided in its central region with an annular, radial extension 124 which is connected via a third control or.
  • Pressure supply line 134 is permanently connected to the low pressure outlet 24 of the pressure supply unit 23.
  • the movable control edge 128 of the stepped piston 112 is in positive overlap with the control edge 126 fixed to the housing, this overlap ⁇ X1 corresponding to only a small fraction of the stroke X1 that the stepped piston 112 from its illustrated basic position out in the opening direction of the seat valve 96, ie can perform in the direction of arrow 131 and only a small fraction of the stroke X2 that the stepped piston 112 in the opposite direction, i.e. can perform in the direction of arrow 132.
  • the annular chamber 124 delimited by the annular groove-shaped extension 124 and the smaller piston step 109 regardless of the overlap ⁇ X1 of the movable control edge 128 and the control edge 126 fixed to the housing, is not hermetically sealed against the central valve chamber 101, but stands with it a peripheral edge notch 133 with a small overflow cross-section still in communicating connection, which is canceled, however, when the stepped piston has carried out a small fraction ⁇ X2 of its possible stroke in the direction of arrow 131, after which the annular groove-shaped communicating connection with the low-pressure outlet 24 of the pressure supply unit 23 Extension 124 of the smaller bore step 104 is blocked against the central valve chamber 101.
  • the preload of the valve closing spring 92 is or is set so high that the force with which the valve ball 94 is pressed against the circular valve seat 97 approximately corresponds to the force, e.g. 90% of that force corresponds when the valve ball 94 is pressurized within the circular area delimited by the valve seat 97 with a pressure which corresponds to the maximum outlet pressure of the pressure supply unit 23, which can be provided at its high pressure outlet 26.
  • Such a high pressure can be injected into the central valve chamber 101 if the tool 16 - in differential operation of the hydraulic cylinder 13 - is acted upon by the high output pressure P H after the pressure changeover valve 39 has been switched over, and this pressure is also applied to the larger ones via the follow-up control valve 44 Drive pressure chamber 11 of the hydraulic cylinder 13 is coupled.
  • the pretensioning of the closing spring 92 is accordingly set to a value equivalent to a "closing pressure" of 162 bar.
  • the bias of the return spring 117 is negligible and equivalent to a pressure of only a few, for example 5 bar.
  • F4 denotes the amount of the circular area bordered by the valve seat 97, within which the pressure on the valve ball 94, which is coupled via the first hydraulic control line 103 into the central valve chamber 101 of the area changeover valve 42, can be built up in the annular drive pressure chamber 12 of the hydraulic cylinder 13 can act, and with F5 the cross-sectional area of the larger piston stage 111 of the stepped piston 112, which is acted upon by the outlet pressure P A of the follow-up control valve 44, which is also coupled into the larger drive pressure chamber 11 of the hydraulic cylinder, these surfaces are F4 and F5 the area switching valve 42 dimensioned so that they satisfy the following relationship: F5 / F4> P H / P N (8th) P H and P N denote the values of the outlet pressure of the pressure supply unit 23 at its high-pressure outlet 26 and at its low-pressure outlet 24, which are in the ratio 3/1 to one another
  • the annular chamber 124 of the surface changeover valve 42 is connected via a first control line 134 to the smaller control pressure chamber 69 of the pressure changeover valve 39.
  • control chamber 114 of the surface changeover valve 42 which is movably delimited by the larger piston stage 111, is connected to the larger control pressure chamber 71 of the pressure changeover valve 39 via a second control line 136.
  • the area ratio F1 / F2 of the drive hydraulic cylinder 13 has the value 2 and that the larger piston area 27 designated by F1 of the piston 21 of the drive hydraulic cylinder 13 has an amount of 100 cm2.
  • the control device 10 which is specified in more detail both in terms of its basic structure and by means of a special exemplary embodiment, operates more specifically as follows in a typical work cycle:
  • the follow-up control valve is - initially - in order to bring the tool 16 of the hydraulic cylinder 13 into a defined starting position - for example in its upper end position controlled in its functional position designated II.
  • the larger diameter control pressure chamber 71 of the pressure changeover valve 39 which is connected via the second control line 116 of the pressure changeover valve 39 to the control chamber 114 of the surface changeover valve 42, which through the larger piston stage 111 of the stepped piston 112 of the surface changeover valve 42 is movably limited, is also relieved of pressure to the tank 43 of the pressure supply unit 23, with the result that the pressure changeover valve 39 is held in its - shown in FIG. 1 - basic position, in which, via the check valve 58, the - lower - Output pressure of the pressure supply unit 23 is present on the one hand at the supply pressure connection 57 of the follow-up control valve and on the other hand is directly coupled into the annular radial extension 124 of the surface switch valve 42.
  • This functional position of the surface changeover valve 42 in combination with the functional position II of the overrun control valve 44 also corresponds to the withdrawal operation of the hydraulic cylinder 13, through which it returns to its starting position after the tool 16 has carried out its working stroke.
  • the overrun control valve 44 is switched to its functional position I by actuating the stepping motor 46 with the “forward” control pulse sequence 49.
  • both the larger, upper, drive pressure chamber 11 of the hydraulic cylinder 13 and the control chamber 114 of the surface switchover valve and the larger control pressure chamber 71 of the pressure switchover valve 39 are acted upon by the outlet pressure P A of the follow-up control valve 44, which affects the open state of the flow - Flow path 54 of the follow-up control valve can be regulated as required.
  • the follow-up control valve 44 as a result of the now increasing follow-up error between the stepper motor-controlled position setpoint specification and the means the feedback device 52 detected actual position of the tool 16, the flow cross section of the flow flow path 54 increases, with the result that the pressure in the larger drive pressure chamber 11 of the hydraulic cylinder 13 and thus also in the larger control pressure chamber 71 of the pressure changeover valve 39 and in the control chamber 114 of the surface switching valve 42 rises.
  • the stepped piston 112 of the surface switching valve 42 is now relieved of pressure, as it were, since it has almost the same pressures both via the central valve chamber 101 and the annular chamber 115 and via the - lower - control chamber 114, which amounts to the high output pressure P H of the pressure supply unit 23 or almost this value P H correspond, is exposed, and insofar as it is "neutral" pressurized.
  • the relatively weak return spring 117 is capable of displacing the stepped piston 112 in the direction of the valve ball 64 and bringing it into contact with the valve ball 94, ie into the position shown in FIG. 1.
  • a factor is designated which is less than 1 and the area ratio f1 / f2 of the areas f1 and f2 of the end flanges 67 and 68 of the valve slide 66 of the pressure changeover valve 39 corresponds.
  • Functional values of the parameter b 1 are between 0.85 and 0.95, preferably around 0.9.
  • the switchover of the surface switchover valve 42 should, after it has been in its position providing the pressure relief of the smaller drive pressure chamber 12 of the hydraulic cylinder 13, at an operating pressure value P AF which is lower than the value P N. b1.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Forging (AREA)
  • Control Of Presses (AREA)
  • Press Drives And Press Lines (AREA)
  • Auxiliary Drives, Propulsion Controls, And Safety Devices (AREA)
  • Vehicle Body Suspensions (AREA)
EP89104861A 1988-04-29 1989-03-18 Hydraulische Steuereinrichtung für die Antriebssteuerung eines doppelt-wirkenden Hydrozylinders Expired - Lifetime EP0339247B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89104861T ATE92804T1 (de) 1988-04-29 1989-03-18 Hydraulische steuereinrichtung fuer die antriebssteuerung eines doppelt-wirkenden hydrozylinders.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3814580A DE3814580A1 (de) 1988-04-29 1988-04-29 Hydraulische steuereinrichtung fuer die antriebssteuerung eines doppelt-wirkenden hydrozylinders
DE3814580 1988-04-29

Publications (2)

Publication Number Publication Date
EP0339247A1 EP0339247A1 (de) 1989-11-02
EP0339247B1 true EP0339247B1 (de) 1993-08-11

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EP89104861A Expired - Lifetime EP0339247B1 (de) 1988-04-29 1989-03-18 Hydraulische Steuereinrichtung für die Antriebssteuerung eines doppelt-wirkenden Hydrozylinders

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Country Link
US (1) US5042362A (pt)
EP (1) EP0339247B1 (pt)
JP (1) JPH0696200B2 (pt)
AT (1) ATE92804T1 (pt)
BR (1) BR8901797A (pt)
DE (2) DE3814580A1 (pt)
ES (1) ES2043923T3 (pt)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE59305912D1 (de) * 1993-02-02 1997-04-24 Putzmeister Maschf Verfahren zum fördern von vorzerkleinerten metallschrott oder dergleichen festkörper enthaltenden dickstoffen
DE4412224A1 (de) * 1994-04-09 1995-10-12 Graebener Pressensysteme Gmbh Presse für eine Kaltverformung von Metallwerkstücken
DE19829679A1 (de) * 1998-07-03 2000-01-05 Hartmann & Laemmle Hydraulische Antriebseinrichtung für eine Widerstands-Schweißmaschine
AU9634998A (en) * 1998-10-21 2000-05-08 Bronx Engineering Company Limited, The Roll forming line with punching tool
US6939120B1 (en) * 2002-09-12 2005-09-06 Komag, Inc. Disk alignment apparatus and method for patterned media production
US20040132301A1 (en) * 2002-09-12 2004-07-08 Harper Bruce M. Indirect fluid pressure imprinting
DE102004024354A1 (de) * 2003-05-16 2005-01-05 Bosch Rexroth Ag Antrieb für eine Stanz- oder Umformmaschine
CN100423934C (zh) * 2003-05-16 2008-10-08 博世力士乐股份有限公司 液压传动装置
US7370569B2 (en) 2003-05-16 2008-05-13 Bosch Rexroth Ag Hydraulic drive
JP4444620B2 (ja) * 2003-10-15 2010-03-31 ナブテスコ株式会社 油圧モータの自動変速機構
DE102004049247A1 (de) * 2004-10-01 2006-04-13 Aesculap Ag & Co. Kg Chirurgisches Instrument
CN101733968B (zh) * 2008-11-04 2014-01-29 昆山施耐特机械有限公司 气液压冲压机接触工件检测机构
CN102641979B (zh) * 2012-05-14 2014-07-16 浙江金瑞五金索具有限公司 可墩两头的冷墩机
CN102744345B (zh) * 2012-07-19 2014-06-11 浙江大学 锻造操作机缓冲缸液压系统
US11110506B2 (en) 2016-10-18 2021-09-07 Barnes Group Inc. Variable pulsating, gap control, auto-learning press cushion device

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US946481A (en) * 1909-06-11 1910-01-11 Ellis Bryan Anderson Automatic change-valve for presses.
US2356366A (en) * 1942-12-04 1944-08-22 Hydraulic Machinery Inc Power transmission
CH459766A (de) * 1967-05-12 1968-07-15 Huegi Wilfried Hydraulische Presse mit einem doppelt wirkenden Presskolben
US3604884A (en) * 1969-04-24 1971-09-14 Essar Corp Electrode feed control for edm machine
FR2242234A1 (en) * 1973-08-27 1975-03-28 Experimentalmy Inst Kuznechno Hydraulic press with pulsating drive - high pressure feed line and outlet line connected to pulsator
AT328296B (de) * 1973-11-22 1976-03-10 Ruthner Industrieanlagen Ag Steuerung fur hydraulische pressen mit mehreren presskolben
DE2645849A1 (de) * 1976-10-11 1978-04-13 Osterwalder Ag Hydraulisch angetriebene presse
US4216702A (en) * 1978-05-01 1980-08-12 Eaton Yale Ltd. Pressure sensing regenerative hydraulic system
DE3521579A1 (de) * 1985-06-15 1986-12-18 J.M. Voith Gmbh, 7920 Heidenheim Steuerventil
DE3715261C1 (en) * 1987-05-08 1988-10-13 Schirmer Plate Und Siempelkamp Open-die forging press

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105522094A (zh) * 2014-09-29 2016-04-27 天津市天锻压力机有限公司 基于中压电机驱动比例泵的恒功率控制方法

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US5042362A (en) 1991-08-27
DE3814580A1 (de) 1989-11-09
JPH01299800A (ja) 1989-12-04
ATE92804T1 (de) 1993-08-15
EP0339247A1 (de) 1989-11-02
JPH0696200B2 (ja) 1994-11-30
DE58905209D1 (de) 1993-09-16
ES2043923T3 (es) 1994-01-01
BR8901797A (pt) 1989-11-28

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