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EP0288719A2 - 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
EP0288719A2
EP0288719A2 EP88104223A EP88104223A EP0288719A2 EP 0288719 A2 EP0288719 A2 EP 0288719A2 EP 88104223 A EP88104223 A EP 88104223A EP 88104223 A EP88104223 A EP 88104223A EP 0288719 A2 EP0288719 A2 EP 0288719A2
Authority
EP
European Patent Office
Prior art keywords
piston
pressure
displacement
actuating
control device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP88104223A
Other languages
German (de)
English (en)
Other versions
EP0288719A3 (en
EP0288719B1 (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 and hydraulically with great force over short distances by means of a displacement piston, the displacement piston in turn being pneumatically actuatable via the pressure intensifier .
  • Such a control device is known from DE-OS 28 18 337.
  • 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 significantly 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 occurs 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 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 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.
  • actuating rod is coupled to a displacement measuring unit and that the actuating pressure of the working piston is adjustable independently of the actuating pressure of the displacement piston as a function of an output signal from the displacement measuring unit.
  • 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 displacement piston with pressure intensifier has a single action, and the actuation pressure of the pressure intensifier is set by means of an electropneumatic 2/2-way valve with pilot valve.
  • This measure has the advantage that the high force of the actuating rod can be adjusted precisely.
  • the working piston can be extended in rapid traverse with low force until a first output signal of the displacement measuring unit is reached, and then the displacement piston can be extended with high force in slow speed until a second signal is reached.
  • the second signal is a second output signal of the displacement measuring unit.
  • This measure has the advantage that tasks can be carried out in which the actuating rod has to travel a certain distance with high force without the actuation pressure being important, as is the case e.g. is the case with joining work.
  • the actuating pressure of the displacement piston is measured by means of a pressure sensor and compared with a predetermined actuating pressure interval.
  • This measure has the advantage that it can be monitored whether an actuating pressure had to be applied to measure the above-mentioned 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 as part of a joining work, falling below the interval would mean that the parts to be joined were imprecise in the sense that they fit too loosely into one another 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 narrow 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 actuating pressure of the displacement piston.
  • 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 closely.
  • 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. 4, 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 profiles.
  • 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 power drive 14 which is known per se, 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 electropneumatic 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 separates 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 travel through 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 force amplifier 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 arm 19 emits a signal s with the displacement measuring unit 20, which is fed to the controller 72 via the signal line 73.
  • the signal s is compared in the comparators 81 and 84 with the kort predetermined target values s a and s e .
  • 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 setpoint p a .
  • the 2/2 switching valve 66 switches over and the slow power stroke is ended.
  • an interval 95a is defined with comparators 88a, 91a and threshold value stages 89a, 92a, in this case, however, an interval of the path which lies between a lower limit value s u and an upper limit s o . Otherwise, the logic corresponds to the elements in the lower half of FIG. 3.

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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)
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
DE19873710178 DE3710178A1 (de) 1987-04-01 1987-04-01 Steuereinrichtung fuer einen pneumo-hydraulischen kraftantrieb
DE3710178 1987-04-01

Publications (3)

Publication Number Publication Date
EP0288719A2 true EP0288719A2 (fr) 1988-11-02
EP0288719A3 EP0288719A3 (en) 1989-07-26
EP0288719B1 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 (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0439433A1 (fr) 1990-01-23 1991-07-31 IMI Norgren AG Distributeur à tiroir pneumatique
WO1993015323A1 (fr) * 1992-02-01 1993-08-05 Malina, Viktor Groupe hydraulique haute pression
FR2955629A1 (fr) * 2010-01-25 2011-07-29 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
WO2013167225A1 (fr) * 2012-05-08 2013-11-14 Tox Pressotechnik Gmbh & Co. Kg Dispositif démultiplicateur de pression hydropneumatique et dispositif de rivetage
FR3012564A1 (fr) * 2013-10-30 2015-05-01 Dassault Aviat Dispositif et procede d'obturation d'une extremite d'un conduit
EP3378581A1 (fr) * 2017-03-24 2018-09-26 Böllhoff Verbindungstechnik GmbH Dispositif d'assemblage en plusieurs étapes et procédé d'assemblage correspondant

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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US4099436A (en) * 1977-04-11 1978-07-11 Donald Joseph Beneteau Apparatus for piercing sheet material
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WO1984000827A1 (fr) * 1982-08-06 1984-03-01 Mts System Corp Circuit de commutation en mode de commande
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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
US4099436A (en) * 1977-04-11 1978-07-11 Donald Joseph Beneteau Apparatus for piercing sheet material
DE2818337B1 (de) * 1978-04-26 1979-10-18 Haug Paul Druckuebersetzter hydropneumatischer Antrieb
DE2925902A1 (de) * 1979-06-27 1981-01-15 Manfred Wanzke Signalvorrichtung zur erzeugung von elektrischen steuersignalen fuer eine steuervorrichtung einer presse
FR2517923A1 (fr) * 1981-12-04 1983-06-10 Darragon Cie Ets E Presse de stratification de circuits imprimes multicouches a systeme de commande hydropneumatique
WO1984000827A1 (fr) * 1982-08-06 1984-03-01 Mts System Corp Circuit de commutation en mode de commande
JPS61148000A (ja) * 1984-12-21 1986-07-05 Hitachi Ltd プレス装置

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EP0439433A1 (fr) 1990-01-23 1991-07-31 IMI Norgren AG Distributeur à tiroir pneumatique
WO1993015323A1 (fr) * 1992-02-01 1993-08-05 Malina, Viktor Groupe hydraulique haute pression
FR2955629A1 (fr) * 2010-01-25 2011-07-29 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
US9816535B2 (en) 2012-05-08 2017-11-14 Tox Pressotechnik Gmbh & Co. Kg Hydropneumatic device for pressure transmission and riveting device
CN104285065A (zh) * 2012-05-08 2015-01-14 托克斯印刷技术有限及两合公司 用于压力传送的液压气动装置和铆接装置
JP2015518429A (ja) * 2012-05-08 2015-07-02 トックス・プレッソテヒニック・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング・ウント・コンパニー・コマンディトゲゼルシャフト 圧力伝達用ハイドロニューマチック装置及びリベット打ち機
WO2013167225A1 (fr) * 2012-05-08 2013-11-14 Tox Pressotechnik Gmbh & Co. Kg Dispositif démultiplicateur de pression hydropneumatique et dispositif de rivetage
FR3012564A1 (fr) * 2013-10-30 2015-05-01 Dassault Aviat Dispositif et procede d'obturation d'une extremite d'un conduit
EP2868959A1 (fr) * 2013-10-30 2015-05-06 Dassault Aviation Dispositif et procédé d'obturation d'une extrémité d'un conduit
US9416907B2 (en) 2013-10-30 2016-08-16 Dassault Aviation Device and method for plugging an end of a conduit
EP3378581A1 (fr) * 2017-03-24 2018-09-26 Böllhoff Verbindungstechnik GmbH Dispositif d'assemblage en plusieurs étapes et procédé d'assemblage correspondant
CN108714676A (zh) * 2017-03-24 2018-10-30 伯尔霍夫连接技术有限公司 多步骤连接装置及其连接方法
US10589341B2 (en) 2017-03-24 2020-03-17 Böllhoff Verbindungstechnik GmbH Multi-step joining device and joining method therefor

Also Published As

Publication number Publication date
ATE88794T1 (de) 1993-05-15
EP0288719A3 (en) 1989-07-26
DE3880545D1 (de) 1993-06-03
EP0288719B1 (fr) 1993-04-28
DE3710178A1 (de) 1988-10-20

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