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EP0288719B1 - Dispositif de commande pour installation de puissance pneumatique-hydraulique - Google Patents

Dispositif de commande pour installation de puissance pneumatique-hydraulique Download PDF

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Publication number
EP0288719B1
EP0288719B1 EP88104223A EP88104223A EP0288719B1 EP 0288719 B1 EP0288719 B1 EP 0288719B1 EP 88104223 A EP88104223 A EP 88104223A EP 88104223 A EP88104223 A EP 88104223A EP 0288719 B1 EP0288719 B1 EP 0288719B1
Authority
EP
European Patent Office
Prior art keywords
pressure
piston
actuation
steering device
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP88104223A
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German (de)
English (en)
Other versions
EP0288719A3 (en
EP0288719A2 (fr
Inventor
Wolf Dieter Prof. Dr. Goedecke
Rolf Schmidt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Vodafone GmbH
Gebrueder Schmidt Fabrik fuer Feinmechanik GmbH and Co KG
Original Assignee
Mannesmann AG
Gebrueder Schmidt Fabrik fuer Feinmechanik GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mannesmann AG, Gebrueder Schmidt Fabrik fuer Feinmechanik GmbH and Co KG filed Critical Mannesmann AG
Priority to AT88104223T priority Critical patent/ATE88794T1/de
Publication of EP0288719A2 publication Critical patent/EP0288719A2/fr
Publication of EP0288719A3 publication Critical patent/EP0288719A3/de
Application granted granted Critical
Publication of EP0288719B1 publication Critical patent/EP0288719B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/032—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters
    • F15B11/0325—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of fluid-pressure converters the fluid-pressure converter increasing the working force after an approach stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/216—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being pneumatic-to-hydraulic converters
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3057—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having two valves, one for each port of a double-acting output member
    • 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/30—Directional control
    • F15B2211/365—Directional control combined with flow control and pressure control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6346—Electronic controllers using input signals representing a state of input means, e.g. joystick position
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6653—Pressure control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press

Definitions

  • the invention relates to a control device for a pneumo-hydraulic power drive with an actuating rod, which can be actuated pneumatically with low force over long distances by means of a working piston in rapid traverse, and hydraulically in short speed with large force can be actuated over short distances with large force by means of a displacement piston, the displacement piston in turn via a Air piston can be actuated pneumatically and together with it forms a pressure intensifier and a first valve arrangement is provided to act on the working piston and a second valve arrangement is provided to act on the air piston.
  • Such a control device is known from DE-B-2818 337.
  • the power drive has a front, double-acting and pneumatically actuated working piston which runs in a cylinder bore with a relatively large diameter and can be pressurized with compressed air from both sides.
  • the working piston carries an actuating rod, which can be used for riveting, for example. If compressed air is applied to the back of the working piston, it travels forward in rapid motion with relatively little force. When an end position is reached, the pressure on the back of the working piston increases. The compressed air now flows onto the back of an air piston of approximately the same cross-section, which in turn carries the displacement piston with a substantially smaller cross-sectional area.
  • the displacer plunges into an oil reservoir which is arranged in the area of the rear of the actuating rod.
  • the switch from rapid traverse with low force to slow speed (power stroke) with high force takes place automatically because, as mentioned, the compressed air from the rear of the working piston automatically reaches the rear of the air piston when a certain value is reached and the power stroke automatically starts.
  • switching valves can also be provided in the known device, the compressed air being passed on to the air piston by a pressure directional control valve, which is then switched over when the pressure at the inlet (rear side of the working piston) exceeds a predetermined amount.
  • a pressure directional control valve which is then switched over when the pressure at the inlet (rear side of the working piston) exceeds a predetermined amount.
  • a path-dependent control in which a limit switch is provided in the movement path of the actuating rod, which switches over from rapid traverse to slow speed (power stroke) when actuated.
  • switching valves are used in all of these controls, and the actuation of the air piston takes place via a forced sequence control depending on the actuation of the working piston.
  • the known device thus has the disadvantage that the transition from rapid to slow speed is always abrupt and the slow speed is uncontrolled, so that the known device cannot be used for a large number of applications when it comes down to the actuating force as a function of predetermined parameters meter or regulate depending on the respective application.
  • the invention is therefore based on the object of developing a device of the type mentioned at the outset such that the operating parameters of the device can be freely specified and in particular can be set in a controlled manner.
  • the rapid traverse can be freely programmed in contrast to the known limit switch.
  • the slow gear power stroke
  • any force / displacement dependencies being specifiable.
  • control device according to the invention can be used for a variety of tasks, not only for relatively rough power work, such as the riveting mentioned above, but also for precise power work, for example when operating a hand of a handling device and the like more.
  • the working piston is double-acting and the actuating pressure of the working piston is set by means of electro-pneumatic 2/2 servo valves.
  • This measure has the advantage that the overdrive of the working piston can be adjusted particularly precisely from the starting position to the end position, because the use of electropneumatic servo valves allows an analog input variable to be converted precisely into a pneumatic output variable.
  • the air piston of the pressure booster is single-acting, and the actuation pressure of the pressure booster is set by means of an electropneumatic 2/2 switching valve with a pilot valve.
  • This measure has the advantage that the high force of the actuating rod can be adjusted precisely.
  • the second signal supplied to the controller is a second output signal from the displacement measuring unit.
  • the actuation pressure of the pressure intensifier is measured by means of a pressure sensor and compared with a predetermined actuation pressure interval.
  • This measure has the advantage that it can be monitored whether an actuation pressure had to be applied in order to measure the aforementioned distance in the power stroke, which pressure was within one specified tolerance range. If, for example, a part is to be pressed into another part in the course of joining work, falling below the interval would mean that the parts to be joined were imprecise in the sense that they fit into each other too loosely and consequently only a slight actuation pressure was required, to measure the given distance, while exceeding the interval indicates that the parts were made too tight and therefore too high an actuation pressure was required to achieve the desired joining. In both cases, this may be unacceptable for the intended use of the parts being joined, so that if the interval is exceeded or fallen short of, the parts joined can be declared as rejects.
  • the second signal is an output signal from a pressure sensor that detects the actuation pressure of the pressure booster.
  • a pressure value to be achieved is specified if, for example, the joining force is specified in the course of joining work.
  • the output signal of the displacement measuring unit can be compared with a predetermined displacement interval.
  • a criterion for a reject part is thus formed by checking whether there is a path within a permissible range until the predetermined pressure value is reached Tolerance range was measured.
  • a too large path would be measured, while conversely only a small path could be measured in the case of parts that were manufactured too tightly.
  • Fig. 1 designates a force unit as a whole, such as e.g. for pressing, embossing and Like. Can be used.
  • a U-shaped portal 11 is placed on a work table 12 which carries a workpiece 13 to be joined.
  • a power drive 14, the details of which will be explained further below in relation to FIG. 2, is provided with valve packs 15 and 16 attached to the side.
  • An actuating rod 17 protrudes from the bottom of the power drive 14 and can be moved vertically depending on the actuation of the valve packages 15, 16.
  • the actuating rod 17 can carry a tool 18, for example an embossing stamp or the like, at its lower axial end.
  • the actuating rod 17 is laterally coupled to an arm 19 which interacts with a displacement measuring unit 20 for the vertical deflection of the actuating rod 17.
  • the distance measuring unit 20 and the valve packages 15, 16 are connected to a control unit 25 via connecting cables 21, 22, 23, 24.
  • the control unit 25 has, for example, a first keyboard 26 for specifying one or more extension paths of the actuating rod 17 and a second keyboard 27, which can be used, for example, for specifying certain actuating forces or path / force curves.
  • a schematically indicated display unit 28 serves to display operating states, operating parameters and. the like
  • the force unit shown in Fig. 1 one wants e.g. can specify that the actuating rod 17 first traverses a large distance in rapid traverse by which it was previously lifted from the workpiece 13 in order to be able to handle it in the region of the work table 12.
  • the actuating rod 17, possibly with a tool 18, is then to travel a certain distance under low force at high speed (typically in the range between 10 and 500 kN).
  • the power unit 10 should be able to be controlled so that the actuating rod 17 either measures a predetermined power stroke, i.e. without influencing the actuating force, provided it does not, of course, exceed a certain limit value, or a certain final force value is to be achieved, without taking into account the stroke required for this.
  • FIG 2 shows further details of the power drive 14 including the associated control.
  • the known power drive 14 has a working piston 40 in the front part, which runs in a first cylinder bore 41 of relatively large diameter. Means a front channel 42 and a rear channel 43, the working piston 40 can be acted upon from both sides with compressed air.
  • a first line 44 is used, which is connected to the front channel 42 and leads to a first electropneumatic 2/2-servo valve 45.
  • a second pneumatic line 46 is connected to the rear channel 43 and leads to a second electro-pneumatic 2/2-servo valve 47.
  • the servo valves 45, 47 are connected via a third line 48 and a fourth line 49 to a common compressed air connection 50, which is typically is supplied with a supply pressure of 5 bar.
  • the actuating rod 17, which is connected to the working piston 40, is provided with a second cylindrical bore 56.
  • a third cylindrical bore 57 the diameter of which corresponds approximately to that of the first cylindrical bore 41, an oil piston 58 runs, which defines in front of it an oil space (storage space) 60 which extends into the second cylindrical bore 56.
  • the oil piston 58 which runs freely in the third cylindrical bore 57, is connected via a helical spring 61 to an air piston 62 which also runs freely in the third cylindrical bore 57.
  • the air piston 62 runs forward into a displacement piston 63, the cross-sectional area of which is substantially smaller than the cross-sectional area of the air piston 62, the oil piston 58 and the working piston 40.
  • the diameter of the displacement piston 63 is slightly smaller than the diameter of the second cylindrical bore 56.
  • the rear side of the air piston 62 can be acted upon by compressed air via a fifth line 65 by means of a channel 64.
  • the fifth line 65 leads to a 2/2 switching valve 66 which is provided with a pilot valve in the illustrated embodiment.
  • a sixth line 67 is connected to the rear channel 43 and is used to supply compressed air to the 2/2-way switching valve 66.
  • a seventh line is indicated, which opens into the space between the oil piston 58 and air piston 62.
  • the seventh line 68 is intended to indicate that the air piston 62 can of course also be double-acting and can be pressurized with compressed air from both sides if this should be cheaper in individual cases.
  • An eighth line 70 leads as a branch line from the sixth line 67 to a pressure sensor 71.
  • the pressure sensor 71 is in turn connected to a controller 72 which receives a further input signal via a signal line 73 from the displacement measuring unit 20.
  • the controller 72 is connected to the keyboards 26, 27 and it has output terminals 74 which lead via the connecting cables 22, 23 to the valve packages 15, 16 or the servo valves 45, 47 and the switching valve 66 contained therein.
  • the user of the force unit 10 prescribes a first path s a , which the actuating rod 17 is to traverse at high speed. After measuring this path s a , a second, smaller path s e should be measured in the power stroke.
  • the pressure p which acts on the air piston 62 and above the pressure intensifier 62/63 can be converted into the force of the actuating rod 17, determined, and a statement is to be made as to whether the pressure p required for measuring the power stroke s e is within a predetermined tolerance between a lower pressure value p u and a upper pressure value p o .
  • the values s a , S e , p u and p o are first entered into the control unit 25 using the keyboards 26, 27.
  • a start signal is first given to a flip-flop 76 via a terminal 75 and the flip-flop 76 is thus set.
  • the flip-flop 76 in turn actuates the second electropneumatic 2/2-servo valve 47, so that compressed air can reach the working piston 40, namely from the right in FIG. 2.
  • the displacement measuring unit 20 is connected to a first comparator 81, the output of which is connected to a first zero detector 82.
  • the zero detector 82 in turn controls the set input of a second flip-flop 83, the output of which in turn actuates the 2/2 switching valve 66.
  • a second comparator 84 is connected on the output side to a second zero detector 85, the output of which is connected to the reset input of the second flip-flop 83.
  • the further inputs of the comparators 81, 82 are formed by terminals 86, 87, to which setpoints, namely a value s a for the end of the rapid traverse and a value s e for the end of the slow traverse, are applied.
  • the pressure sensor 71 is connected to a third comparator 88, the output of which is connected to a first threshold value stage 89.
  • the output of the threshold stage 89 is in turn at the input of an AND gate 90.
  • the pressure sensor 71 is also connected to an input of a fourth comparator 91, the output of which is connected to a second threshold value stage 92. Its output is in turn connected to a second input of the AND gate 90.
  • the further inputs of the comparators 88, 91 are connected to terminals 93, 94 to which setpoints can be applied, namely the lower threshold value P u and the upper threshold value p u of the pressure p.
  • the threshold values of the threshold value stages 89, 92 define a printing interval 95.
  • the output of the AND gate 90 is led to a display 96.
  • the mechanism works as follows: As soon as the working piston 40 moves to the left by setting the first flip-flop 76 in FIG. 2, the arm 19 emits a signal s with the displacement measuring unit 20, which is fed to the controller 72 via the signal line 73. In the controller 72, the signal s is compared in the comparators 81 and 84 with the kort predetermined target values s a and s e . As soon as the target value s a has been reached, ie at the end of the overdrive range, the zero detector 82 responds and sets the second flip-flop 83, which in turn actuates the 2/2 switching valve 66.
  • the second flip-flop 83 is reset via the zero detector 85 and the switching valve 66 is switched over again.
  • the working piston 40 By venting the right side of the working piston 40 while simultaneously applying compressed air via the left channel 42, the working piston 40 can now be moved back to the starting position at high speed.
  • the pressure p on the rear of the air piston 62 was monitored via the pressure sensor 71. If the pressure in this range lies within the interval 95, the display 96 responds because only in this interval the outputs of both threshold value stages 89 and 92 show a positive logic signal, while outside of the interval 95 one of the two threshold value stages shows a negative logic signal leads. This means that when the display 96 was actuated, a workpiece was machined in the target area, while when the display 96 went out, a scrap part was produced.
  • circuit diagram recognizable in FIG. 4 largely corresponds to the circuit diagram of FIG. 3, and corresponding elements are provided with the same reference symbols. Only by adding an "a" are comparable components designated in their function.
  • the driving through the quick passage through the element 81 to 83 by reaching the final value S A is monitored in the manner already described.
  • the reaching of the final value of the power stroke is not monitored via the path but rather via the pressure, specifically in the second comparator 84a, which is connected to a corresponding target value p a .
  • the 2/2 switching valve 66 switches over and the slow power stroke is ended.

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  • Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Servomotors (AREA)
  • Arrangement And Driving Of Transmission Devices (AREA)

Claims (7)

  1. Dispositif de commande d'un entraînement mécanique hydropneumatique (14) déplaçant une tige de travail (17) pneumatiquement sur une longue course à vitesse rapide et puissance réduite, au moyen d'un piston de travail (40) relié à la tige, hydrauliquement sur une faible course à vitesse lente et puissance élevée au moyen d'un piston de refoulement (63), qui peut être lui-même actionné par un piston pneumatique (62) avec lequel il forme un démultiplicateur de pression -62, 63), un premier système de soupapes (15, 45, 47) étant prévu pour actionner le piston de travail (40) et un deuxième (16, 66) pour actionner le piston pneumatique (62), caractérisé en ce que :
    - les deux systèmes de soupapes (15, 45, 47) et (16, 66) sont commandés électriquement,
    - un régulateur (72) est associé à un appareil (26) pour préimposer une avance rapide (sa) de la tige de travail (17) ainsi que la fin de la course lente au moyen d'une seconde valeur imposée (se, pa),
    - la tige de travail (17) et une unité de mesure de déplacement (20) d'une part, cette unité et le régulateur d'autre part, ont leurs fonctionnements associés de sorte que, jusqu'au moment où l'unité de mesure de déplacement (20) émet un premier signal de sortie (sa), la tige de travail (17) se déplace à vitesse rapide sous l'action du piston de travail (40) alimenté par le premier système de soupapes (15, 45, 47), puis jusqu'à ce que soit émis un second signal (se, pa), se déplace à vitesse lente sous l'action du démultiplicateur de pression (62, 63) alimenté par le deuxième système de soupapes (16, 66), le passage de la vitesse rapide à la vitesse lente étant indépendant de la pression actionnant le piston de travail (40).
  2. Dispositif de commande selon la revendication 1, caractérisé en ce que le piston de travail (40) est à double effet et le premier système de soupapes (45, 47), constitué d'un servodistributeur électropneumatique du type à 2/2 voies assure le réglage de la pression d'actionnement du piston de travail.
  3. Dispositif de commande selon la revendication 1 ou 2, caractérisé en ce que le piston pneumatique (62) du démultiplicateur de pression (62, 63) est à simple effet, tandis que le second système de soupapes (16), constitué d'un distributeur électropneumatique de type à 2/2 voies équipé d'une présoupape de commande assure le réglage de la pression d'actionnement du piston de travail.
  4. Dispositif de commande selon la revendication 3, caractérisé en ce que le second signal adressé au régulateur (72) est un second signal de sortie (se) de l'unité de mesure de déplacement.
  5. Dispositif de commande selon la revendication 4, caractérisé en ce qu'il est prévu un capteur de pression (71) déconnectée au point de vue des pressions de multiplicateur de pression (62, 63), ce capteur assurant en permanence la mesure électrique de la pression d'actionnement (p) du démultiplicateur de pression (62, 63) et sa comparaison, dans le régulateur (72) avec les limites d'une plage de valeurs préimposée.
  6. Dispositif de commande selon la revendication 3, caractérisé en ce que le second signal est un signal de sortie (pa) d'un capteur de pression (71) mesurant la pression d'actionnement (p) du démultiplicateur de pression (62, 63).
  7. Dispositif de commande selon la revendication 6, caractérisé en ce que le signal de sortie (sa) de l'unité de mesure de déplacement est comparé aux limites d'une plage de valeurs préimposée (95a) définie par le déplacement maximal admissible de la tige de travail (17).
EP88104223A 1987-04-01 1988-03-17 Dispositif de commande pour installation de puissance pneumatique-hydraulique Expired - Lifetime EP0288719B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88104223T ATE88794T1 (de) 1987-04-01 1988-03-17 Steuereinrichtung fuer einen pneumo-hydraulischen kraftantrieb.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3710178 1987-04-01
DE19873710178 DE3710178A1 (de) 1987-04-01 1987-04-01 Steuereinrichtung fuer einen pneumo-hydraulischen kraftantrieb

Publications (3)

Publication Number Publication Date
EP0288719A2 EP0288719A2 (fr) 1988-11-02
EP0288719A3 EP0288719A3 (en) 1989-07-26
EP0288719B1 true EP0288719B1 (fr) 1993-04-28

Family

ID=6324159

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88104223A Expired - Lifetime EP0288719B1 (fr) 1987-04-01 1988-03-17 Dispositif de commande pour installation de puissance pneumatique-hydraulique

Country Status (3)

Country Link
EP (1) EP0288719B1 (fr)
AT (1) ATE88794T1 (fr)
DE (2) DE3710178A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3378581B1 (fr) 2017-03-24 2020-01-29 Böllhoff Verbindungstechnik GmbH Dispositif d'assemblage en plusieurs étapes et procédé d'assemblage correspondant

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Publication number Priority date Publication date Assignee Title
DE3911033A1 (de) * 1989-04-05 1990-10-11 Oesterr Forsch Seibersdorf Press- bzw. pruefzelle
ATE101901T1 (de) 1990-01-23 1994-03-15 Walter Ag Pneumatisches schieberventil.
WO1993015323A1 (fr) * 1992-02-01 1993-08-05 Malina, Viktor Groupe hydraulique haute pression
FR2955629B1 (fr) * 2010-01-25 2012-03-30 Peugeot Citroen Automobiles Sa Procede et appareil d'assemblage d'une premiere piece sur une seconde piece par engagement en force controle par des mesures en temps reel
DE102012008902A1 (de) * 2012-05-08 2013-11-14 Tox Pressotechnik Gmbh & Co. Kg Hydropneumatische Vorrichtung zur Druckübersetzung und Nietvorrichtung
FR3012564B1 (fr) * 2013-10-30 2015-12-18 Dassault Aviat Dispositif et procede d'obturation d'une extremite d'un conduit

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GB955957A (en) * 1959-05-15 1964-04-22 Normalair Ltd Improvements in or relating to control systems for hydraulic and pneumatic presses
FR1427837A (fr) * 1964-12-21 1966-02-11 Davy & United Eng Co Ltd Dispositif de commande automatique pour un élément animé d'un mouvement de va-et-vient
DE2334499A1 (de) * 1972-07-20 1974-01-31 Von Roll Ag Verfahren und vorrichtung zur herstellung von bloecken
DE2544794B2 (de) * 1975-10-07 1979-11-22 Thyssen Industrie Ag, 4300 Essen Antrieb einer hydraulischen Presse
DE2645849A1 (de) * 1976-10-11 1978-04-13 Osterwalder Ag Hydraulisch angetriebene presse
US4099436A (en) * 1977-04-11 1978-07-11 Donald Joseph Beneteau Apparatus for piercing sheet material
DE2818337C2 (de) * 1978-04-26 1980-07-17 Haug, Paul, 7307 Aichwald Druckübersetzter hydropneumatischer
US4288987A (en) * 1978-11-11 1981-09-15 Eugen Rapp Pneumo-hydraulic booster with rapid-traverse feature
DE2925902A1 (de) * 1979-06-27 1981-01-15 Manfred Wanzke Signalvorrichtung zur erzeugung von elektrischen steuersignalen fuer eine steuervorrichtung einer presse
DE2929616A1 (de) * 1979-07-21 1981-02-12 Haug Paul Druckuebersetzter hydropneumatischer antrieb
FR2517923A1 (fr) * 1981-12-04 1983-06-10 Darragon Cie Ets E Presse de stratification de circuits imprimes multicouches a systeme de commande hydropneumatique
US4458189A (en) * 1982-08-06 1984-07-03 Mts Systems Corporation Control mode switching circuit
DE3347000A1 (de) * 1983-12-24 1985-07-04 Robert Bosch Gmbh, 7000 Stuttgart Elektrohydraulische einrichtung zur steuerung eines doppeltwirkenden hydromotors
DD227058A1 (de) * 1984-10-08 1985-09-11 Warnke Umformtech Veb K Anordnung zum regeln fuer steuerbare pneumatikkissen
JPS61148000A (ja) * 1984-12-21 1986-07-05 Hitachi Ltd プレス装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3378581B1 (fr) 2017-03-24 2020-01-29 Böllhoff Verbindungstechnik GmbH Dispositif d'assemblage en plusieurs étapes et procédé d'assemblage correspondant

Also Published As

Publication number Publication date
ATE88794T1 (de) 1993-05-15
EP0288719A3 (en) 1989-07-26
DE3710178A1 (de) 1988-10-20
DE3880545D1 (de) 1993-06-03
EP0288719A2 (fr) 1988-11-02

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