EP0085080B1 - Control circuit for a pneumo-hydraulic pressure intensifier - Google Patents

Control circuit for a pneumo-hydraulic pressure intensifier Download PDF

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Publication number
EP0085080B1
EP0085080B1 EP82902371A EP82902371A EP0085080B1 EP 0085080 B1 EP0085080 B1 EP 0085080B1 EP 82902371 A EP82902371 A EP 82902371A EP 82902371 A EP82902371 A EP 82902371A EP 0085080 B1 EP0085080 B1 EP 0085080B1
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EP
European Patent Office
Prior art keywords
valve
hydraulic
control valve
pressure
cylinder
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
Application number
EP82902371A
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German (de)
French (fr)
Other versions
EP0085080A1 (en
EP0085080A4 (en
Inventor
Béla ZIMBER
Imre Molnar
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.)
KOEZPONTI VALTO-ES HITELBANK RT INNOVACIOS ALAP
Original Assignee
KOZPONTI VALTO-ES HITELBANK RT INNOVACIOS ALAP
Kozponti Valto-Es Hitelbank Rt Innovacios Alap
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Priority to AT82902371T priority Critical patent/ATE19292T1/en
Publication of EP0085080A1 publication Critical patent/EP0085080A1/en
Publication of EP0085080A4 publication Critical patent/EP0085080A4/en
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Publication of EP0085080B1 publication Critical patent/EP0085080B1/en
Expired 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
    • F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
    • F15B11/072—Combined pneumatic-hydraulic systems
    • F15B11/0725—Combined pneumatic-hydraulic systems with the driving energy being derived from a pneumatic system, a subsequent hydraulic system displacing or controlling the output element
    • 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
    • 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
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • 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
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F15B2211/40584—Assemblies of multiple valves the flow control means arranged in parallel with a check 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve

Definitions

  • the invention relates to a control circuit for a pneumatic-hydraulic pressure intensifier for actuating hydraulic working devices, which has a double-acting pneumatic drive piston and a displacement piston which can be immersed in a hydraulic pressure chamber to which the hydraulic working device is connected.
  • the object of the invention is to provide a control circuit for a pneumatic-hydraulic pressure intensifier with a double-acting pneumatic drive piston and a displacement piston which can be immersed in a hydraulic pressure chamber, and to design it in such a way that different hydraulic working devices can be actuated via the pressure intensifier in a specific mode of operation to be performed that can be easily adapted to the respective work device.
  • control circuits such as quick exhaust valves, timers, throttle check valves and the like. Like., are generally known. It is also known per se (DE-B-15 50 716) for a pneumatic-hydraulic pressure intensifier whose pneumatic drive piston is only single-acting to use a pneumatically actuated hydraulic container as the hydraulic pressure source.
  • the pressure intensifier with a control circuit can be used to actuate hydraulic working devices for riveting, pressing, cutting, for sheet metal forming, for lifting, tensioning, driving in screws, removing hubs, etc.
  • the mode of operation corresponding to the respective requirement can be set.
  • the different ways of working can be varied as desired.
  • the pneumatically controlled pressure intensifier 1 has a double working cylinder, on one side of which a working cylinder receiving the pneumatically operated double-acting drive piston 1a, and on the other side of which a hydraulic pressure chamber is arranged, in which the displacement piston 1 b, which is assembled with the drive piston 1 a, can be immersed.
  • the two-position control valve 9 is connected to the primary space of the pneumatic working cylinder in front of the drive piston 1 a of the pressure intensifier 1 via the control line 21.
  • the control valve 9 is connected to a compressed air source via an air conditioner.
  • the control valve 9 is connected to the pilot valve 11 via the control line 22 and the valve 10.
  • the other side of the pilot valve 11 is connected via line 24 to line 21, which in turn connects the control valve 9 to the primary space of the pneumatic working cylinder.
  • Another connection of the control valve 9 is connected to the directional control valve 8 via the throttle check valve 7.
  • a buffer tank 25 is connected to the line between the throttle check valve 7 and the directional valve 8.
  • the pressure line 27 branches off from the additional line 26 between the control valve 9 and the directional control valve 8, which is connected via the directional control valve 8 to the secondary space formed behind the drive piston 1a of the pneumatic working cylinder, which leads via the quick-release valve 3 to the hydraulic reservoir 2.
  • the line between the directional control valve 8 and the secondary space is connected via the control line 28 to the signal input of the valve 10, on the one hand, and on the other hand it is connected to the control valve 9 via the throttle check valve 6.
  • the buffer tank 30 is connected between the throttle check valve 6 and the control valve 9.
  • the hydraulic tank 2 is connected via the throttle check valve 4 to the hydraulic pressure chamber of the pressure booster 1 in such a way that this connection can be shut off by the displacement piston 1.
  • this is achieved in that the hydraulic cylinder is formed in two parts and a sealed passage for the displacer 1 is formed between the two parts.
  • different hydraulic working devices see FIGS. 3a to 3j
  • the hydraulic reservoir 2 is connected via the throttle check valve 4 and the directional control valve 12 to the line 29 connecting the directional control valve 12 to the hydraulic pressure chamber.
  • the directional control valve 12 is a valve which determines the mode of operation, i. H. it ensures either a single cycle or a repetitive function depending on the actuation of the pilot valve.
  • the compressed air holds the pneumatic drive piston 1a in its basic position with a pressure of 6 bar via the control valve 9.
  • the control valve 9 receives the control pressure denoted by X via the valve 10 and the control line 22.
  • the control valve 9 switches over, whereby the primary space of the pneumatic working cylinder is connected to the atmosphere and the compressed air reaches the hydraulic tank 2 via the quick exhaust valve 3.
  • the compressed air supplies a control pressure Z for the directional control valve 8 via the throttle check valve 7.
  • the directional control valve 8 switches over, as a result of which the compressed air reaches the secondary space of the pneumatic working cylinder and displaces the drive piston 1a to the front.
  • the compressed air in the hydraulic tank 2 presses oil under a pressure of 6 bar via the throttle check valve 4 into the hydraulic pressure chamber or through it into the connected working device.
  • the working device makes an impact movement, ie it moves forward as long as the pressure can maintain the movement. This phase can be seen as the delivery of the working device.
  • the displacer 1 b first blocks the path of the liquid flowing out of the hydraulic container 2 and subsequently introduces oil into the working device under a pressure of approximately 150 bar; as a result, it performs the work cycle (cutting, pressing, etc.).
  • the displacer 1b continues until the working device reaches a closed state or until the control valve 9 receives the control pressure Y via the throttle check valve 6.
  • the buffer tank 30 is connected to the line between the throttle check valve 6 and the control valve 9, as a result of which the system functions as a time valve. Now the control valve 9 switches back.
  • the time t 1 elapsed between the pressing of the start button and the appearance of the control pressure Y (FIG. 2) can be regulated by means of the throttle check valve 6.
  • the time t 2 of the rapid advancement of the working device or the movement to the infeed is determined by the appearance of the control pressure Z, which can be set with the throttle check valve 7.
  • the feed speed of the displacer 1 is set with the throttle valve 5; the rapid feed rate t 2 is determined with the help of the throttle check valve 4.
  • the quantity valves 4, 5 determine the speed, while the time is determined by the quantity valves 6, 7, in place of which a time valve of any type can be used.
  • the quantity valves 4, 5, 6, 7 mentioned a wide variety of operating modes are possible. Some examples of these variations are shown in Fig. 2 represented by path-time diagrams.
  • the pistons return to their basic position after the end of a movement phase.
  • the return of the pistons is not connected to the automatic return of the working device to the starting position, since the return check is prevented by the check valve present in the directional control valve 12.
  • This operation can e.g. B. may be required when lifting, tensioning or pulling off a hub.
  • the control signal Y appears on the control valve 9, this switches back to its starting position; as a result, the control system is vented and the drive piston 1a of the pressure intensifier 1 returns to its basic position under the action of the air entering the primary space of the pneumatic cylinder.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

Pneumatically controlled pressure transducer intended to actuate hydraulic working members and provided with a double motor cylinder; on one side thereof there is a pneumatically actuated cylinder, and on the other side a hydraulically actuated cylinder; it is also provided with hydraulic working means connected to the hydraulic side. The invention is characterized by the presence of a control valve connected to the primary chamber which is before the piston of the pneumatic cylinder of the motor cylinder, valve which is in operation relationship with a starting valve while being connected by a choke retainer valve with another valve, and being also connected through a draining valve with the hydraulic tank, respectively by the valve with the secondary chamber of the pneumatic cylinder. Another essential characteristic consists in that the control valve is connected by the choke retainer valve of the hydraulic tank with the hydraulic cylinder of the double motor cylinder, thereby allowing an obturation by means of the hydraulic piston. The conduit located between the valve and the cylinder is in control relationship with the control valve through an additional choke retainer valve. The pressure transducer according to the invention is a relatively economical device having a unitary and simple structure, by means of which a large variety of hydraulic working members may be actuated in a way which is determined by the working members applied as well as by the operation mode subject to the work to be performed.

Description

Die Erfindung betrifft eine Steuerschaltung für einen pneumatisch-hydraulischen Druckübersetzer zur Betätigung hydraulischer Arbeitsvorrichtungen, der einen doppeltwirkenden pneumatischen Antriebskolben und einen Verdrängerkolben aufweist, der in einen hydraulischen Druckraum eintauchbar ist, an welchen die hydraulische Arbeitsvorrichtung angeschlossen ist.The invention relates to a control circuit for a pneumatic-hydraulic pressure intensifier for actuating hydraulic working devices, which has a double-acting pneumatic drive piston and a displacement piston which can be immersed in a hydraulic pressure chamber to which the hydraulic working device is connected.

In der Industrie und auch auf sonstigen Gebieten ist es recht oft erforderlich, die verschiedensten Stoffe bearbeiten zu müssen ; als solche Arbeitsprozesse sollen z. B. das Zuschneiden, das Abscheren, die Blechverformung, das Spannen, Pressen, Nieten, Eintreiben von Schrauben, Ziehverfahren, Abziehen von Naben usw. erwähnt werden. Diese Arbeiten werden unter Zuhilfenahme verschiedener Spezialmaschinen durchgeführt. Jedoch ist der Einsatz einer derartigen Spezialmaschine erst dann wirtschaftlich, wenn sie entsprechend ausgelastet wird. Andererseits können zu oben genannten Arbeiten bestimmte Handwerkzeuge infolge der mit ihnen ausübbaren begrenzten Kraft nur eingeschränkt verwendet werden. Es besteht jedoch auch die Möglichkeit, hydraulische Arbeitsvorrichtungen zu verwenden, die über einen pneumatisch-hydraulischen Druckübersetzer beispielsweise derart betrieben werden, daß der Hydraulikdruck von einem geringen Wert für eine Zustellbewegung der Arbeitsvorrichtung mit Hilfe des Druckübersetzers auf einen höheren Wert für den Arbeitstakt der Arbeitsvorrichtung gesteigert wird.In industry and in other areas, it is quite often necessary to process a wide variety of substances; as such work processes should B. cutting, shearing, sheet metal forming, clamping, pressing, riveting, driving screws, pulling method, pulling off hubs, etc. are mentioned. This work is carried out with the help of various special machines. However, the use of such a special machine is only economical if it is used accordingly. On the other hand, certain hand tools can only be used to a limited extent due to the limited force that can be exerted with them. However, there is also the possibility of using hydraulic working devices which are operated via a pneumatic-hydraulic pressure intensifier, for example in such a way that the hydraulic pressure increases from a low value for an infeed movement of the working device with the aid of the pressure intensifier to a higher value for the working cycle of the working device becomes.

Dies läßt sich grundsätzlich mit einem bekannten Druckübersetzer (FR-A-22 29 876) der im einleitenden Teil des Patentanspruchs 1 angegebenen Art erreichen. Der bekannte Druckübersetzer ist mit dem hydraulischen Arbeitszylinder der Arbeitsvorrichtung als Baueinheit zusammengebaut. Jedoch bleibt die spezielle Ausbildung der zugehörigen Steuerschaltung in der genannten Druckschrift weitestgehend offen, denn es ist lediglich angegeben, daß der doppeltwirkende pneumatische Antriebskolben des Druckübersetzers mit einem üblichen 4-Wege-Steuerventil gesteuert wird und der hydraulische Teil von einer Druckflüssigkeitsquelle gespeist wird.This can basically be achieved with a known pressure intensifier (FR-A-22 29 876) of the type specified in the introductory part of patent claim 1. The known pressure intensifier is assembled as a structural unit with the hydraulic working cylinder of the working device. However, the special design of the associated control circuit in the cited document remains largely open, because it is only stated that the double-acting pneumatic drive piston of the pressure booster is controlled with a conventional 4-way control valve and the hydraulic part is fed by a hydraulic fluid source.

Durch die Erfindung wird die Aufgabe gelöst, eine Steuerschaltung für einen pneumatisch-hydraulischen Druckübersetzer mit doppeltwirkendem pneumatischen Antriebskolben und in einen hydraulischen Druckraum eintauchbaren Verdrängerkolben zu schaffen und so auszubilden, daß über den Druckübersetzer unterschiedliche hydraulische Arbeitsvorrichtungen in von der durchzuführenden Arbeit bestimmter Betriebsweise betätigt werden können, die an die jeweilige Arbeitsvorrichtung leicht angepaßt werden kann.The object of the invention is to provide a control circuit for a pneumatic-hydraulic pressure intensifier with a double-acting pneumatic drive piston and a displacement piston which can be immersed in a hydraulic pressure chamber, and to design it in such a way that different hydraulic working devices can be actuated via the pressure intensifier in a specific mode of operation to be performed that can be easily adapted to the respective work device.

Dies wird gemäß der Erfindung durch die Merkmale der Steuerschaltung aus dem Anspruch 1 erreicht. Bevorzugte Ausgestaltungen der Erfindung sind aus den Unteransprüchen ersichtlich.This is achieved according to the invention by the features of the control circuit from claim 1. Preferred embodiments of the invention can be seen from the subclaims.

Die erfindungsgemäß verwendeten Elemente der Steuerschaltung, wie Schnellentlüftungsventile, Zeitglieder, Drosselrückschlagventile u. dgl., sind für sich allgemein bekannt. Auch ist es an sich bekannt (DE-B-15 50 716), für einen pneumatisch-hydraulischen Druckübersetzer, dessen pneumatischer Antriebskolben jedoch nur einfachwirkend ist, als hydraulische Druckquelle einen pneumatisch beaufschlagbaren Hydraulikbehälter zu verwenden.The elements of the control circuit used according to the invention, such as quick exhaust valves, timers, throttle check valves and the like. Like., Are generally known. It is also known per se (DE-B-15 50 716) for a pneumatic-hydraulic pressure intensifier whose pneumatic drive piston is only single-acting to use a pneumatically actuated hydraulic container as the hydraulic pressure source.

Der Druckübersetzer mit einer erfindungsgemäßen Steuerschaltung kann zum Betätigen von hydraulischen Arbeitsvorrichtungen zum Nieten, Pressen, Zuschneiden, zur Blechverformung, zum Heben, Spannen, Eintreiben von Schrauben, Abziehen von Naben usw. verwendet werden. Durch die Einstellung der Drossel-Rückschlagventile kann die dem jeweiligen Erfordernis entsprechende Betriebsweise eingestellt werden, so z. B. der schnelle Vorlauf für das Zustellen, der einen hohen Kraftaufwand beanspruchende Arbeitstakt z. B. zum Abschneiden von Blechen, zum Heben usw., und zuletzt der Rücklauf der Arbeitsvorrichtung mit einer beliebigen Geschwindigkeit. Selbstverständlich können die verschiedenen Arbeitsweisen beliebig variiert werden.The pressure intensifier with a control circuit according to the invention can be used to actuate hydraulic working devices for riveting, pressing, cutting, for sheet metal forming, for lifting, tensioning, driving in screws, removing hubs, etc. By adjusting the one-way flow control valves, the mode of operation corresponding to the respective requirement can be set. B. the fast forward for the delivery, the high workload z. B. for cutting sheet metal, for lifting, etc., and finally the return of the working device at any speed. Of course, the different ways of working can be varied as desired.

Die Erfindung wird anhand der Zeichnung für ein Ausführungsbeispiel näher erläutert. Es zeigen :

  • Figur 1 die schematische Schaltungsanordnung der erfindungsgemäßen Steuerschaltung eines pneumatisch-hydraulischen Druckübersetzers,
  • Figur 2 Weg-Zeitdiagramme von vier Betriebsweisen,
  • Figur 3a die schematische Darstellung einer Niet- und Preßvorrichtung,
  • Figur 3b die schematische Darstellung einer Schneid- und Abschervorrichtung,
  • Figur 3c eine Arbeitsvorrichtung zur Blechverformung,
  • Figur 3d eine Hebevorrichtung,
  • Figur 3e eine Spann- und Zuschneidvorrichtung,
  • Figur 3f eine zum Eintreiben von Schrauben dienende Arbeitsvorrichtung,
  • Figur 3g eine Arbeitsvorrichtung zum Anziehen von Muttern,
  • Figur 3h eine Arbeitsvorrichtung für das Abziehen einer Nabe,
  • Figur 3i eine Nietziehvorrichtung und
  • Figur 3j eine Platten-Kneifschneidvorrichtung.
The invention is explained in more detail with reference to the drawing for an exemplary embodiment. Show it :
  • 1 shows the schematic circuit arrangement of the control circuit according to the invention of a pneumatic-hydraulic pressure booster,
  • FIG. 2 path-time diagrams of four operating modes,
  • 3a shows the schematic representation of a riveting and pressing device,
  • FIG. 3b the schematic representation of a cutting and shearing device,
  • FIG. 3c shows a working device for sheet metal deformation,
  • FIG. 3d a lifting device,
  • FIG. 3e a tensioning and cutting device,
  • FIG. 3f shows a working device used to drive in screws,
  • 3g shows a working device for tightening nuts,
  • FIG. 3h shows a working device for pulling off a hub,
  • Figure 3i a rivet pulling device and
  • Figure 3j, a plate pinch cutting device.

Wie aus Fig. 1 ersichtlich, weist der pneumatisch gesteuerte Druckübersetzer 1 einen doppelten Arbeitszylinder auf, an dessen einen Seite ein den pneumatisch betätigten doppeltwirkenden Antriebskolben 1a aufnehmender Arbeitszylinder, und an dessen anderen Seite ein hydraulischer Druckraum angeordnet sind, in welchen der Verdrängerkolben 1 b, der mit dem Antriebskolben 1a zusammengebaut ist, eintauchen kann. Mit dem primären Raum des pneumatischen Arbeitszylinders vor dem Antriebskolben 1a des Druckübersetzers 1 ist das Zweistellungs-Steuerventil 9 über die Steuerleitung 21 verbunden. Das Steuerventil 9 ist über einen Luftaufbereiter an eine Druckluftquelle angeschlossen. Das Steuerventil 9 ist über die Steuerleitung 22 und das Ventil 10 mit dem Vorsteuerventil 11 verbunden. Die andere Seite des Vorsteuerventils 11 ist über die Leitung 24 an die Leitung 21 angeschlossen, die ihrerseits das Steuerventil 9 mit dem primären Raum des pneumatischen Arbeitszylinders verbindet.As can be seen from FIG. 1, the pneumatically controlled pressure intensifier 1 has a double working cylinder, on one side of which a working cylinder receiving the pneumatically operated double-acting drive piston 1a, and on the other side of which a hydraulic pressure chamber is arranged, in which the displacement piston 1 b, which is assembled with the drive piston 1 a, can be immersed. The two-position control valve 9 is connected to the primary space of the pneumatic working cylinder in front of the drive piston 1 a of the pressure intensifier 1 via the control line 21. The control valve 9 is connected to a compressed air source via an air conditioner. The control valve 9 is connected to the pilot valve 11 via the control line 22 and the valve 10. The other side of the pilot valve 11 is connected via line 24 to line 21, which in turn connects the control valve 9 to the primary space of the pneumatic working cylinder.

Ein weiterer Anschluß des Steuerventils 9 ist über das Drossel-Rückschlagventil 7 mit dem Wegeventil 8 verbunden. An die Leitung zwischen dem Drossel-Rückschlagventil 7 und dem Wegeventil 8 ist ein Pufferbehälter 25 angeschlossen. Von der zusätzlichen Leitung 26 zwischen dem Steuerventil 9 und dem Wegeventil 8, die über das Wegeventil 8 an den hinter dem Antriebskolben 1a des pneumatischen Arbeitszylinders ausgebildeten Sekundärraum angeschlossen ist, ist die Druckleitung 27 abgezweigt, die über das Schnellentlüftungsventil 3 zu dem Hydraulikbehälter 2 führt. Die zwischen dem Wegeventil 8 und dem Sekundärraum vorhandene Leitung steht über die Steuerleitung 28 einerseits mit dem Signaleingang des Ventils 10 in Verbindung, andererseits ist sie über das Drossel-Rückschlagventil 6 mit dem Steuerventil 9 verbunden. Zwischen dem Drossel-Rückschlagventil 6 und dem Steuerventil 9 ist der Pufferbehälter 30 angeschlossen.Another connection of the control valve 9 is connected to the directional control valve 8 via the throttle check valve 7. A buffer tank 25 is connected to the line between the throttle check valve 7 and the directional valve 8. The pressure line 27 branches off from the additional line 26 between the control valve 9 and the directional control valve 8, which is connected via the directional control valve 8 to the secondary space formed behind the drive piston 1a of the pneumatic working cylinder, which leads via the quick-release valve 3 to the hydraulic reservoir 2. The line between the directional control valve 8 and the secondary space is connected via the control line 28 to the signal input of the valve 10, on the one hand, and on the other hand it is connected to the control valve 9 via the throttle check valve 6. The buffer tank 30 is connected between the throttle check valve 6 and the control valve 9.

Der Hydraulikbehälter 2 ist über das Drossel-Rückschlagventil 4 mit dem hydraulischen Druckraum des Druckübersetzers 1 derart verbunden, daß diese Verbindung von dem Verdrängerkolben 1 abgesperrt werden kann. Bei dem Ausführungsbeispiel ist dies dadurch verwirklicht, daß der hydraulische Zylinder zweiteilig ausgebildet ist und zwischen den beiden Teilen ein abgedichteter Durchgang für den Verdrängerkolben 1 ausgebildet ist. Unter Zwischenschaltung des Wegeventils 12 können an den hydraulischen Druckraum unterschiedliche hydraulische Arbeitsvorrichtungen (siehe Fig. 3a bis 3j) angeschlossen werden. Der Hydraulikbehälter 2 ist über das Drossel-Rückschlagventil 4 und das Wegeventil 12 mit der das Wegeventil 12 mit dem hydraulischen Druckraum verbindenden Leitung 29 verbunden. Das Wegeventil 12 ist ein die Betriebsweise bestimmendes Ventil, d. h. es stellt entweder einen einmaligen Takt oder eine sich mehrmals wiederholende Funktion in Abhängigkeit von der Betätigung des Vorsteuerventils sicher.The hydraulic tank 2 is connected via the throttle check valve 4 to the hydraulic pressure chamber of the pressure booster 1 in such a way that this connection can be shut off by the displacement piston 1. In the embodiment, this is achieved in that the hydraulic cylinder is formed in two parts and a sealed passage for the displacer 1 is formed between the two parts. With the interposition of the directional control valve 12, different hydraulic working devices (see FIGS. 3a to 3j) can be connected to the hydraulic pressure chamber. The hydraulic reservoir 2 is connected via the throttle check valve 4 and the directional control valve 12 to the line 29 connecting the directional control valve 12 to the hydraulic pressure chamber. The directional control valve 12 is a valve which determines the mode of operation, i. H. it ensures either a single cycle or a repetitive function depending on the actuation of the pilot valve.

In der Grundstellung des pneumatisch-hydraulischen Druckübersetzers 1 hält die Druckluft den pneumatischen Antriebskolben 1a mit einem Druck von 6 bar über das Steuerventil 9 in seiner Grundstellung. Wird nun der Startknopf des Vorsteuerventils 11 einmal gedrückt, erhält das Steuerventil 9 über das Ventil 10 und die Steuerleitung 22 den mit X bezeichneten Steuerdruck. Unter der Wirkung des Steuerdrucks X schaltet das Steuerventil 9 um, wodurch der primäre Raum des pneumatischen Arbeitszylinders mit der Atmosphäre verbunden wird und die Druckluft über das Schnellentlüftungsventil 3 in den Hydraulikbehälter 2 gelangt. Außerdem liefert die Druckluft über das Drossel-Rückschlagventil 7 einen Steuerdruck Z für das Wegeventil 8. Unter der Wirkung des Steuerdrucks Z schaltet das Wegeventil 8 um, wodurch die Druckluft in den Sekundärraum des pneumatischen Arbeitszylinders gelangt und den Antriebskolben 1a nach vorn verschiebt. Bis zu diesem Zeitpunkt wird von der Druckluft in dem Hydraulikbehälter 2 Öl unter einem Druck von 6 bar über das Drossel-Rückschlagventil 4 in den hydraulischen Druckraum hineingedrückt bzw. durch denselben in die angeschlossene Arbeitsvorrichtung. Unter der Wirkung des hydraulischen Drucks führt die Arbeitsvorrichtung eine Stoßbewegung aus, d. h. sie bewegt sich solange vorwärts, wie der Druck die Bewegung aufrechterhalten kann. Diese Phase kann als Zustellung der Arbeitsvorrichtung betrachtet werden. Während seines Vorschiebens sperrt der Verdrängerkolben 1 b zuerst den Weg der aus dem Hydraulikbehälter 2 ausströmenden Flüssigkeit ab und führt darauffolgend Öl unter einem Druck von etwa 150 bar in die Arbeitsvorrichtung ein ; als Ergebnis führt diese den Arbeitstakt (Schneiden, Pressen usw.) durch. Der Verdrängerkolben 1b schreitet solange fort, bis die Arbeitsvorrichtung einen geschlossenen Zustand erreicht bzw. bis das Steuerventil 9 über das Drossel-Rückschlagventil 6 den Steuerdruck Y erhält. An die Leitung zwischen dem Drossel-Rückschlagventil 6 und dem Steuerventil 9 ist der Pufferbehälter 30 angeschlossen, wodurch das System als Zeitventil funktioniert. Jetzt schaltet das Steuerventil 9 zurück. Die zwischen dem Drücken des Startknopfes bis zum Erscheinen des Steuerdruckes Y abgelaufene Zeit t1 (Fig. 2) kann mittels des Drossel-Rückschlagventils 6 geregelt werden. Die Zeit t2 des schnellen Vorschubs der Arbeitsvorrichtung bzw. der Bewegung bis zur Zustellung wird durch das Erscheinen des Steuerdrucks Z bestimmt, was mit dem Drossel-Rückschlagventil 7 eingestellt werden kann. Die Vorschubgeschwindigkeit des Verdrängerkolbens 1 wird mit dem Drosselventil 5 eingestellt; die schnelle Vorschubgeschwindigkeit t2 wird mit Hilfe des Drossel-Rückschlagventils 4 bestimmt.In the basic position of the pneumatic-hydraulic pressure intensifier 1, the compressed air holds the pneumatic drive piston 1a in its basic position with a pressure of 6 bar via the control valve 9. If the start button of the pilot valve 11 is now pressed once, the control valve 9 receives the control pressure denoted by X via the valve 10 and the control line 22. Under the action of the control pressure X, the control valve 9 switches over, whereby the primary space of the pneumatic working cylinder is connected to the atmosphere and the compressed air reaches the hydraulic tank 2 via the quick exhaust valve 3. In addition, the compressed air supplies a control pressure Z for the directional control valve 8 via the throttle check valve 7. Under the action of the control pressure Z, the directional control valve 8 switches over, as a result of which the compressed air reaches the secondary space of the pneumatic working cylinder and displaces the drive piston 1a to the front. Up to this point, the compressed air in the hydraulic tank 2 presses oil under a pressure of 6 bar via the throttle check valve 4 into the hydraulic pressure chamber or through it into the connected working device. Under the action of the hydraulic pressure, the working device makes an impact movement, ie it moves forward as long as the pressure can maintain the movement. This phase can be seen as the delivery of the working device. During its advancement, the displacer 1 b first blocks the path of the liquid flowing out of the hydraulic container 2 and subsequently introduces oil into the working device under a pressure of approximately 150 bar; as a result, it performs the work cycle (cutting, pressing, etc.). The displacer 1b continues until the working device reaches a closed state or until the control valve 9 receives the control pressure Y via the throttle check valve 6. The buffer tank 30 is connected to the line between the throttle check valve 6 and the control valve 9, as a result of which the system functions as a time valve. Now the control valve 9 switches back. The time t 1 elapsed between the pressing of the start button and the appearance of the control pressure Y (FIG. 2) can be regulated by means of the throttle check valve 6. The time t 2 of the rapid advancement of the working device or the movement to the infeed is determined by the appearance of the control pressure Z, which can be set with the throttle check valve 7. The feed speed of the displacer 1 is set with the throttle valve 5; the rapid feed rate t 2 is determined with the help of the throttle check valve 4.

Wie aus dem Gesagten hervorgeht, wird von den Mengenventilen 4, 5 die Geschwindigkeit bestimmt, während die Zeit von den Mengenventilen 6, 7 bestimmt wird, an deren Stelle ein Zeitventil irgendeines Typs eingesetzt werden kann. Mit den erwähnten vier Mengenventilen 4, 5, 6, 7 werden die verschiedensten Betriebsweisevariationen ermöglicht. Einige Beispiele für diese Variationen sind in Fig. 2 anhand von Weg-Zeitdiagrammen dargestellt.As can be seen from what has been said, the quantity valves 4, 5 determine the speed, while the time is determined by the quantity valves 6, 7, in place of which a time valve of any type can be used. With the four quantity valves 4, 5, 6, 7 mentioned, a wide variety of operating modes are possible. Some examples of these variations are shown in Fig. 2 represented by path-time diagrams.

Während der beschriebenen Betriebsweise kehren die Kolben nach Beendigung einer Bewegungsphase in ihre Grundstellung zurück. Beim Umschalten des Wegeventils 12 ist die Rückkehr der Kolben nicht mit der automatischen Rückstellung der Arbeitsvorrichtung in die Ausgangsstellung verbunden, da die Rückkehr von dem in dem Wegeventil 12 vorhandenen Rückschlagventil verhindert wird. Dieser Arbeitsvorgang kann z. B. beim Heben, Spannen oder Abziehen einer Nabe erforderlich sein. Wenn das Steuersignal Y an dem Steuerventil 9 erscheint, schaltet dieses in seine Ausgangsstellung zurück ; als Ergebnis wird das Steuersystem entlüftet und der Antriebskolben 1a des Druckübersetzers 1 kehrt unter der Wirkung der in den primären Raum des pneumatischen Arbeitszylinders gelangenden Luft in seine Grundstellung zurück.During the described mode of operation, the pistons return to their basic position after the end of a movement phase. When the directional control valve 12 is switched over, the return of the pistons is not connected to the automatic return of the working device to the starting position, since the return check is prevented by the check valve present in the directional control valve 12. This operation can e.g. B. may be required when lifting, tensioning or pulling off a hub. When the control signal Y appears on the control valve 9, this switches back to its starting position; as a result, the control system is vented and the drive piston 1a of the pressure intensifier 1 returns to its basic position under the action of the air entering the primary space of the pneumatic cylinder.

Wenn nun der Startknopf des Vorsteuerventils 11 mehrfach nacheinander gedrückt wird, findet die kontinuierliche Wiederholung der Arbeitsgänge statt. Ein solcher Arbeitsgang wird z. B. bei den kontinuierlichen Schneiden von Blechen erforderlich. Eine derartige Betriebsweise ist in den Weg-Zeitdiagrammen 111, IV veranschaulicht.If the start button of the pilot valve 11 is pressed several times in succession, the operations are continuously repeated. Such an operation is such. B. required for the continuous cutting of sheet metal. Such an operating mode is illustrated in the path time diagrams 111, IV.

Claims (4)

1. Control circuit for pneumatic-hydraulic pressure transmitter (1) provided with a double- acting pneumatic driving piston (1a) and a displacement piston (1b) immersible into a hydraulic pressure chamber, wherein a control valve (9) is provided for pressurising and venting the pneumatic cylinder spaces of the pressure transmitter (1) and a source (2) of hydraulic pressure is connected with the hydraulic pressure chamber such that at the start of an operating cycle the pressure of a hydraulic medium provided by the source (2) of pressure is transmitted to a hydraulically actuated operating machine connected to the transmitter (1) and during the period of pressure transmission the hydraulic pressure chamber is separated from the source (2) of pressure, characterised in that the control valve (9) is pneumatically servocontrolled, in a first switching position connects a primary space for the return stroke of the pneumatic piston (1a) to a source of compressed air and effects venting of the secondary space, and in a second switching position vents the primary space and effects pressurising of the secondary space ; that for changing over the control valve (9) from the first into the second switching position there is provided an arbitrarily actuatable servo-valve (11) the pressure coupling of which is connected to a duct (21) between the control valve (9) and the primary space ; that between the control valve (9) and the secondary space there is a time delay valve (7, 8, 25) provided with a displacement valve (8) operating as an opener ; that for resetting the control valve (9) into its first position there is a control pipe line (28) which is branched off between the displacement valve (8) and the secondary space with a time delay valve (6, 30) ; and that the source of hydraulic pressure is a pneumatically operable hydraulic vessel (2) hydraulically connected to the hydraulic pressure space of the pressure transmitter (1) via a throttle relief valve (4) with intake throttling, the pneumatic operation of the vessel in the second switching position of the control valve (9) ensuing by way of a pressure duct (27) branched off from the duct (26) between control valve (9) and the displacement valve (8), a rapid-acting venting valve (3) being inserted into the pressure duct on change-over of the control valve (9) into the first switching position for rapid venting of the hydraulic vessel (2).
2. Control circuit according to claim 1, characterised in that a valve (10) operating as a closer is interposed between the servo-valve (11) and the control valve (9) the signal input of which is coupled to the connecting duct between the displacement valve (8) and the secondary space.
3. Control valve circuit according to claim 1 or 2, characterised in that the timing valves (7, 8, 25 ; 6, 30) are provided with respective throttle non- return valves (6, 7) and the throttling of the non- return valves (4, 6, 7) is at least partially adjustable.
4. Control valve circuit according to one of claims 1 to 3, characterised in that a 4/2-way displacement valve (12) is arranged at the hydraulic outlet (29) of the pressure transmitter (1) which valves permit in one switching position free throughflow between the pressure transmitter (1) and the processing machine in both directions and in the other switching position allows free throughflow only from the pressure transmitter (1) to the processing machine and from a connection with the hydraulic vessel (2) only from the latter to the hydraulic outlet (29) of the pressure transmitter (1).
EP82902371A 1981-08-04 1982-08-04 Control circuit for a pneumo-hydraulic pressure intensifier Expired EP0085080B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82902371T ATE19292T1 (en) 1981-08-04 1982-08-04 CONTROL CIRCUIT FOR A PNEUMATIC-HYDRAULIC PRESSURE CONVERTER.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
HU812257A HU185642B (en) 1981-08-04 1981-08-04 Penumatically controlled pressure converter for operating hydraulic work devices
HU225781 1981-08-04

Publications (3)

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EP0085080A1 EP0085080A1 (en) 1983-08-10
EP0085080A4 EP0085080A4 (en) 1984-01-20
EP0085080B1 true EP0085080B1 (en) 1986-04-16

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ID=10958536

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EP82902371A Expired EP0085080B1 (en) 1981-08-04 1982-08-04 Control circuit for a pneumo-hydraulic pressure intensifier

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US (1) US4509330A (en)
EP (1) EP0085080B1 (en)
JP (1) JPS58501333A (en)
DE (1) DE3270622D1 (en)
FI (1) FI75214C (en)
HU (1) HU185642B (en)
WO (1) WO1983000540A1 (en)

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IT207878Z2 (en) * 1986-03-06 1988-02-22 Iveco Fiat HYDRAULIC PNEUMO CONVERTER FOR DISC BRAKE CALIPERS
DE3611438A1 (en) * 1986-04-05 1987-10-08 Medical Res & Dev Ag Pneumatic/hydraulic converter
US4879875A (en) * 1988-03-22 1989-11-14 The Boeing Company Fastener driving tool
DK171121B1 (en) * 1989-08-15 1996-06-17 Johannes Vagn Baatrup Hydraulic pressure amplifier
DE4221638B4 (en) * 1992-07-02 2005-11-03 Tox Pressotechnik Gmbh & Co. Kg Method for a hydraulic pressure booster
AT406984B (en) * 1998-12-22 2000-11-27 Joerg Thurner DEVICE FOR CONVERTING ENERGY STORED IN COMPRESSED AIR IN MECHANICAL WORK
EP2368046A4 (en) * 2008-12-10 2013-03-20 Numatics Inc Pressurized air-spring return cylinder and pneumatic intensifier system
ITMO20100044A1 (en) * 2010-02-26 2011-08-27 De Hieronymis Carlo Maria Rozzi HYDRAULIC STRENGTHENING INTENSIFIER WITH MAINTENANCE OF THE REACHED POSITION AND THE PUSHING STRENGTH OBTAINED DURING EVERY RESCUE PHASE
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CN103586995A (en) * 2013-11-12 2014-02-19 乐山市新联机械制造有限责任公司 Gas-liquid pressurization device for discharge door of internal mixer
WO2020178832A1 (en) * 2019-03-05 2020-09-10 Dan Davidian System and method for hydraulic-pneumatic drive with energy storage for elevators

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Also Published As

Publication number Publication date
EP0085080A1 (en) 1983-08-10
JPS58501333A (en) 1983-08-11
FI831086L (en) 1983-03-30
US4509330A (en) 1985-04-09
DE3270622D1 (en) 1986-05-22
HU185642B (en) 1985-03-28
EP0085080A4 (en) 1984-01-20
FI831086A0 (en) 1983-03-30
WO1983000540A1 (en) 1983-02-17
FI75214B (en) 1988-01-29
FI75214C (en) 1988-05-09

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