EP1269026A2 - Hydraulic pressure intensifier - Google Patents

Hydraulic pressure intensifier

Info

Publication number
EP1269026A2
EP1269026A2 EP01940104A EP01940104A EP1269026A2 EP 1269026 A2 EP1269026 A2 EP 1269026A2 EP 01940104 A EP01940104 A EP 01940104A EP 01940104 A EP01940104 A EP 01940104A EP 1269026 A2 EP1269026 A2 EP 1269026A2
Authority
EP
European Patent Office
Prior art keywords
working
space
pressure
piston
pressure intensifier
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
EP01940104A
Other languages
German (de)
French (fr)
Other versions
EP1269026B1 (en
Inventor
Eugen Rapp
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.)
Tox Pressotechnik GmbH and Co KG
Original Assignee
Tox Pressotechnik 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 Tox Pressotechnik GmbH and Co KG filed Critical Tox Pressotechnik GmbH and Co KG
Publication of EP1269026A2 publication Critical patent/EP1269026A2/en
Application granted granted Critical
Publication of EP1269026B1 publication Critical patent/EP1269026B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/214—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being hydrotransformers
    • 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41527—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve
    • F15B2211/41536—Flow control characterised by the connections of the flow control means in the circuit being connected to an output member and a directional control valve being connected to multiple ports of an 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
    • F15B2211/40—Flow control
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in 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
    • F15B2211/76—Control of force or torque of the 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
    • F15B2211/70—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 is based on a hydraulic pressure intensifier according to the type of the main claim.
  • a hydraulic pressure intensifier of the generic type (DE-OS 42 23 41 1)
  • the piston spindle of the plunger is actuated via a pneumatic drive piston to generate the high pressure.
  • a pneumatic supply for this pressure intensifier which is not available in some cases or is always associated with certain circumstances and makes the use of the device dependent on such an air supply.
  • the hydraulic pressure intensifier according to the invention with the characterizing features of the main claim has the advantage of being independent of a compressed air supply and of being always available Energy, namely the electric current, to be supplied.
  • the hydraulics or pneumatics are controlled via valves, which in turn supply the pressure intensifier with media, namely pressure and hydraulic oil, of the energy input (DE-OS 26 25 884 ).
  • the hydraulics only within the pressure intensifier for converting the piston movement driven with relatively little force to a hydraulic high pressure, with corresponding driving force of the working piston.
  • the drive means used is an electric motor, which can be configured in a wide variety of ways, the decisive factor being that at least indirectly there is a stroke, i.e. a linear movement of the drive spindle or the plunger, and then for the working stroke of the piston rod.
  • a ball screw motor or the like serves as the electrical drive means.
  • the electric motor is designed as a linear motor, in which the armature is at least indirectly connected to the plunger or the drive spindle connected to it and / or the piston rod of the working piston, so that, above all, the rapid traverse can take place through the linear forces and the drive spindle can serve as the armature of the linear motor.
  • the rapid traverse before the working stroke and / or the return stroke after the working stroke is at least partially effected hydraulically.
  • annular space for hydraulic control is present within the housing and around the piston rod and, to a limited extent, through the working piston.
  • the hydraulic servo function thereby enabled allows the use of known means, such as servo motors and the like.
  • an annular piston sealed to the drive spindle and to the housing is axially displaceable around the drive spindle, which limits a compensation chamber filled with hydraulic fluid to the accumulator piston and which on the side facing away from the accumulator piston by a spring determining the hydraulic low pressure is burdened, and which is connected to the hydraulic connection. Due to the spring, this compensation space 14 causes a uniform pressure in the storage space and in the annular space, at least during the return stroke.
  • a control valve is arranged in the hydraulic connection between the storage space and the annular space or compensation space, which controls as a one-way valve in the flow direction from the annular space or storage space, but throttles in the flow direction to these spaces.
  • the drive spindle or the piston rod can be driven by a linear motor, as already indicated above.
  • FIG. 1 shows a hydroelectric pressure intensifier in longitudinal section
  • FIG. 2 shows a corresponding alternative example in a greatly simplified manner.
  • a piston rod 3 is driven via a working piston 2 and a hydraulic working space 4 is provided.
  • a storage space 5 is provided, which is connected to the working space 4 by a control bore 6 and is delimited by a storage piston 7.
  • a plunger 8 is provided coaxially with the accumulator piston 7, which plunger is connected to a drive spindle 9 which, after covering a certain stroke, dips into the control bore 6, blocks it and, when the stroke continues in the working space 4, a corresponding to the diameter ratio of the plunger 8 and the working piston 2 given high pressure.
  • a drive spindle 9 is attached to the storage piston 7 in the axial line with the plunger 8, which drives through a linear motor 11, which is arranged outside the housing 1 and is fastened to it.
  • a linear motor 11 which is arranged outside the housing 1 and is fastened to it.
  • the stroke of this plunger 8 is continued via the linear motor to generate a high pressure in the working space 4 and a corresponding advance of the piston rod 3.
  • an annular piston 12 is coaxial with the drive spindle 9 axially displaceably arranged on the latter, which is loaded by a spring 13 and which on the side facing away from the spring 13 delimits an equalizing space 14 which on the other hand is delimited by the storage piston 7.
  • This compensation space 14 is connected via a line 15 both to the storage space 5 and to an annular space 16, which is formed between the working piston 2, the housing 1 and the piston rod 3.
  • Control valves 17 are arranged in the line sections once to the annular space 16 and to the storage space 5, each of which has a free flow to the storage space 5 and the annular space 16 ensure, however, throttle the flow in the opposite direction, this throttling is adjustable. While the current to these rooms serves the return stroke of the device, the throttling effect occurs during the rapid traverse or working stroke of the pressure intensifier.
  • the piston rod 3 can also be actuated via a spindle drive 18 which is only shown in principle and which is designed in particular as a linear motor.
  • a servo motor 19 an additional accumulator 21 for hydraulic fluid and an asynchronous motor 22 can be removed in FIG. 2, which actuates a spindle drive 23 of the spindle 24, which in turn is connected to the plunger 8 with the same axis.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Actuator (AREA)
  • Electromagnetic Pumps, Or The Like (AREA)
  • Hydraulic Motors (AREA)

Abstract

The invention relates to a hydroelectric pressure intensifier in which the plunger piston (8) and/or the driving spindle (9) of said plunger piston and/or the piston rod (3) of the working piston (2) are driven by electrical means, especially electromotors such as linear motors (11).

Description

Hydraulischer DruckύbersetzerHydraulic pressure converter
Stand der TechnikState of the art
Die Erfindung geht aus von einem hydraulischen Druckübersetzer nach Gattung des Hauptanspruchs. Bei einem bekannten hydraulischen Druckübersetzer der gattungsgemäßen Art (DE-OS 42 23 41 1) wird zur Erzeugung des Hochdrucks die Kolbenspindel des Tauchkolbens über einen pneumatischen Antriebskolben betätigt. Hierdurch besteht eine direkte Abhängigkeit von einer pneumatischen Versorgung dieses Druckübersetzer, die in manchen Fällen nicht gegeben ist, bzw. stets mit gewissen Umständen verbunden ist und den Einsatz des Gerätes von einer solchen Luftversorgung abhängig macht.The invention is based on a hydraulic pressure intensifier according to the type of the main claim. In a known hydraulic pressure intensifier of the generic type (DE-OS 42 23 41 1), the piston spindle of the plunger is actuated via a pneumatic drive piston to generate the high pressure. As a result, there is a direct dependency on a pneumatic supply for this pressure intensifier, which is not available in some cases or is always associated with certain circumstances and makes the use of the device dependent on such an air supply.
Die Erfindung und ihre VorteileThe invention and its advantages
Der erfindungsgemäße hydraulische Druckübersetzer mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, von einer Druckluftversorgung unabhängig zu sein und von einer stets zur Verfügung stehenden Energie, nämlich dem elektrischen Strom, versorgt zu werden. Im Gegensatz hierzu stehen solche Anlagen, wie auch oben genannte zum Stand der Technik gehörende Anlagen, bei denen über Ventile die Hydraulik oder Pneumatik gesteuert wird, die wiederum den Druckübersetzer mit Medien, nämlich Druck und Hydrauliköl eingegebener Energie versorgen (DE-OS 26 25 884). Auch hier besteht der Nachteil der belastenden Abhängigkeit von derartigen Energieversorgern im Gegensatz zur Erfindung, bei der die Hydraulik lediglich innerhalb des Druckübersetzers zur Umsetzung der mit verhältnismäßig geringer Kraft angetriebenen Kolbenbewegung zu einem hydraulischen Hochdruck, mit entsprechender Antriebskraft des Arbeitskolbens. Bereits geringe, über elektrische Energie erzeugte, Hubkräfte genügen, um den hydraulischen Hochdruck zu erzeugen. Hierbei ist durchaus denkbar, dass auch die durch die elektrische Energie in den elektrischen Arbeitsmitteln erzeugte Antriebskraft gesteuert wird, beispielsweise indem für den Eilgang eine geringere Kraft erzeugt wird und bei Eintauchen des Tauchkolbens in den Arbeitsraum und aufgrund des dadurch dort gegebenen höheren Drucks, bzw. mechanischen Vorgangs, eine elektrische Umschaltung erfolgt. Auch dies ist ein zusätzlicher Vorteil der erfinderischen Lösung.In contrast, the hydraulic pressure intensifier according to the invention with the characterizing features of the main claim has the advantage of being independent of a compressed air supply and of being always available Energy, namely the electric current, to be supplied. In contrast to this there are such systems, as also the above-mentioned systems belonging to the prior art, in which the hydraulics or pneumatics are controlled via valves, which in turn supply the pressure intensifier with media, namely pressure and hydraulic oil, of the energy input (DE-OS 26 25 884 ). Here too there is the disadvantage of the stressful dependency on such energy suppliers, in contrast to the invention, in which the hydraulics only within the pressure intensifier for converting the piston movement driven with relatively little force to a hydraulic high pressure, with corresponding driving force of the working piston. Even small lifting forces generated by electrical energy are sufficient to generate the hydraulic high pressure. It is quite conceivable that the driving force generated by the electrical energy in the electrical work equipment is also controlled, for example by generating a lower force for the rapid traverse and when the plunger plunges into the work space and because of the higher pressure or the resulting pressure there. mechanical process, an electrical switchover takes place. This is also an additional advantage of the inventive solution.
Nach einer vorteilhaften Ausgestaltung der Erfindung dient als Antriebsmittel ein Elektromotor, der in unterschiedlichster Weise ausgestaltet sein kann, maßgebend ist, dass zumindest mittelbar ein Hub, also eine Linearbewegung der Antriebsspindel, bzw. des Tauchkolbens, und dann für den Arbeitshub, der Kolbenstange erfolgt.According to an advantageous embodiment of the invention, the drive means used is an electric motor, which can be configured in a wide variety of ways, the decisive factor being that at least indirectly there is a stroke, i.e. a linear movement of the drive spindle or the plunger, and then for the working stroke of the piston rod.
Nach einer diesbezüglichen vorteilhaften Ausgestaltung der Erfindung dient als elektrisches Antriebsmittel ein Kugelspindelmotor odgl. Auch hier gibt es außer Kugelspindeln und Trapezspindeln die verschiedensten Ausführungen, bei denen durch die Anordnung der Spindelwand und des Antriebmittels die Drehbewegung des Motors in eine Linearbewegung der Antriebsspindel umgesetzt wird. Nach einer alternativen Ausgestaltung der Erfindung ist der Elektromotor als Linearmotor ausgebildet, bei dem der Anker mindestens mittelbar mit dem Tauchkolben oder der mit diesem verbundenen Antriebsspindel und /oder der Kolbenstange des Arbeitskolbens verbunden ist, so dass vor allem der Eilgang durch die Linearkräfte erfolgen kann und wobei die Antriebsspindel als Anker des Linearmotors dienen kann. Bei der Verwendung eines solchen Linearmotors an der Kolbenstange können nach Eintauchen des Tauchkolbens in den Arbeitsraum am Linearmotor gegebene Halte kräfte, aufgrund der hohen Druckübersetzung, leicht überwunden werden, wobei vor allem beim Eilgang und Rückhub eine schnelle Verstellung möglich ist.According to an advantageous embodiment of the invention in this regard, a ball screw motor or the like serves as the electrical drive means. In addition to ball spindles and trapezoidal spindles, there are also various designs in which the arrangement of the spindle wall and the drive means converts the rotary movement of the motor into a linear movement of the drive spindle. According to an alternative embodiment of the invention, the electric motor is designed as a linear motor, in which the armature is at least indirectly connected to the plunger or the drive spindle connected to it and / or the piston rod of the working piston, so that, above all, the rapid traverse can take place through the linear forces and the drive spindle can serve as the armature of the linear motor. When using such a linear motor on the piston rod, given immersion forces can be easily overcome after immersing the plunger in the working area on the linear motor, due to the high pressure ratio, can be easily overcome, especially with rapid traverse and return stroke, a quick adjustment is possible.
Nach einer zusätzlichen vorteilhaften Ausgestaltung der Erfindung wird der vor dem Arbeitshub liegende Eilgang und/ oder nach dem Arbeitshub liegende Rückhub mindestens teilweise hydraulisch bewirkt.According to an additional advantageous embodiment of the invention, the rapid traverse before the working stroke and / or the return stroke after the working stroke is at least partially effected hydraulically.
Nach einer diesbezüglichen vorteilhaften Ausgestaltung der Erfindung ist innerhalb des Gehäuses und um die Kolbenstange sowie begrenzt durch den Arbeitskolben ein Ringraum zur hydraulischen Steuerung vorhanden. Die hierdurch ermöglichte, hydraulische Servofunktion lässt die Anwendung bekannter Mittel, wie Servomotor und dergleichen zu.According to an advantageous embodiment of the invention in this regard, an annular space for hydraulic control is present within the housing and around the piston rod and, to a limited extent, through the working piston. The hydraulic servo function thereby enabled allows the use of known means, such as servo motors and the like.
Nach einer diesbezüglichen vorteilhaften Ausgestaltung der Erfindung besteht zwischen Ringraum und Speicherraum eine hydraulische Verbindung.According to an advantageous embodiment of the invention in this regard, there is a hydraulic connection between the annular space and the storage space.
Nach einer diesbezüglichen zusätzlichen Ausgestaltung der Erfindung ist um die Antriebsspindel ein zur Antriebsspindel und zum Gehäuse hin abgedichteter Ringkolben axial verschiebbar angeordnet, welcher einen, mit Hydraulikflüssigkeit gefüllten, Ausgleichsraum zum Speicherkolben hin begrenzt und welcher auf der dem Speicherkolben abgewandten Seite durch eine den Hydraulikniederdruck bestimmenden Feder belastet ist, und welcher mit der hydraulischen Verbindung verbunden ist. Dieser Ausgleichsraum 14 bewirkt aufgrund der Feder einen gleichmäßigen Druck im Speicherraum und im Ringraum, zumindest während des Rückhubs.According to an additional embodiment of the invention in this regard, an annular piston sealed to the drive spindle and to the housing is axially displaceable around the drive spindle, which limits a compensation chamber filled with hydraulic fluid to the accumulator piston and which on the side facing away from the accumulator piston by a spring determining the hydraulic low pressure is burdened, and which is connected to the hydraulic connection. Due to the spring, this compensation space 14 causes a uniform pressure in the storage space and in the annular space, at least during the return stroke.
Nach einer diesbezüglichen vorteilhaften Ausgestaltung der Erfindung ist in der hydraulischen Verbindung zwischen Speicherraum und Ringraum, bzw. Ausgleichsraum jeweils ein Steuerventil angeordnet, welches als Einwegventil in Strömungsrichtung aus Ringraum oder Speicherraum heraus sperrt, hingegen in Strömungsrichtung zu diesen Räumen drosselt.According to an advantageous embodiment of the invention in this regard, a control valve is arranged in the hydraulic connection between the storage space and the annular space or compensation space, which controls as a one-way valve in the flow direction from the annular space or storage space, but throttles in the flow direction to these spaces.
Nach einer zusätzlichen vorteilhaften Ausgestaltung der Erfindung ist die Antriebsspindel, bzw. die Kolbenstange durch einen Linearmotor antreibbar, wie oben bereits angedeutet.According to an additional advantageous embodiment of the invention, the drive spindle or the piston rod can be driven by a linear motor, as already indicated above.
Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Beschreibung der Zeichnung und den Ansprüchen entnehmbar.Further advantages and advantageous embodiments of the invention can be found in the following description of the drawing and the claims.
Zeichnungdrawing
Zwei Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und im folgenden näher beschrieben. Es zeigen: Fig. 1 ein hydroelektrischer Druckübersetzer im Längsschnitt und Fig. 2 stark vereinfacht ein entsprechendes Alternativbeispiel.Two embodiments of the invention are shown in the drawing and described in more detail below. 1 shows a hydroelectric pressure intensifier in longitudinal section and FIG. 2 shows a corresponding alternative example in a greatly simplified manner.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Die bei den beiden Ausführungsbeispielen vorhandenen gleichen Bauteile oder Bauteile gleicher Funktion sind im Folgenden mit derselben Bezugsziffer bezeichnet. In einem Gehäuse 1 eines hydraulischen Druckübersetzers ist über einen Arbeitskolben 2 eine Kolbenstange 3 angetrieben und ein hydraulischer Arbeitsraum 4 vorgesehen. Außerdem ist ein Speicherraum 5 vorgesehen, der mit dem Arbeitsraum 4 durch eine Steuerbohrung 6 verbunden ist und durch einen Speicherkolben 7 begrenzt ist. Koaxial mit dem Speicherkolben 7 ist ein Tauchkolben 8 vorgesehen, der mit einer Antriebsspindel 9 verbunden ist, der nach Zurücklegung eines bestimmten Hubes in die Steuerbohrung 6 taucht, diese sperrt und bei Fortsetzung des Hubes im Arbeitsraum 4 einen entsprechend dem Durchmesserverhältnis von Tauchkolben 8 und Arbeitskolben 2 gegebenen Hochdruck erzeugt. Während eines ersten Hubes, nämlich dem Eilgang, wird die Kolbenstange 3 an das Werkstück herangefahren, wonach dann über den Tauchkolben 8 ein Krafthub erzeugt wird zur Bearbeitung des Werkstücks, beispielsweise einer Stanzung derselben.The same components or components with the same function that are present in the two exemplary embodiments are identified below with the same reference number. In a housing 1 of a hydraulic pressure intensifier, a piston rod 3 is driven via a working piston 2 and a hydraulic working space 4 is provided. In addition, a storage space 5 is provided, which is connected to the working space 4 by a control bore 6 and is delimited by a storage piston 7. A plunger 8 is provided coaxially with the accumulator piston 7, which plunger is connected to a drive spindle 9 which, after covering a certain stroke, dips into the control bore 6, blocks it and, when the stroke continues in the working space 4, a corresponding to the diameter ratio of the plunger 8 and the working piston 2 given high pressure. During a first stroke, namely the rapid traverse, the piston rod 3 is moved towards the workpiece, after which a force stroke is then generated via the plunger 8 for machining the workpiece, for example punching it.
Bei dem in Fig. 1 dargestellten Ausführungsbeispiel ist mit dem Speicherkolben 7 in axialer Linie mit dem Tauchkolben 8 eine Antriebsspindel 9 befestigt, die einen Linearmotor 1 1 durchdringt, der außerhalb des Gehäuses 1 angeordnet und an diesem befestigt ist. Sobald die Kolbenstange 3 den Eilhub beendet hat und der Tauchkolben 8 in die Steuerbohrung 6 getaucht ist, wird der Hub dieses Tauchkolbens 8 über den Linearmotor fortgesetzt, zur Erzeugung eines Hochdrucks im Arbeitsraum 4 und einem entsprechenden Vorschub der Kolbenstange 3. Koaxial zur Antriebsspindel 9 ist auf dieser ein Ringkolben 12 axial verschiebbar angeordnet, der durch eine Feder 13 belastet ist und der auf jener der Feder 13 abgewandten Seite einen Ausgleichsraum 14 begrenzt, welcher andererseits durch den Speicherkolben 7 begrenzt ist. Dieser Ausgleichsraum 14 ist über eine Leitung 15 sowohl mit dem Speicherraum 5 als auch mit einem Ringraum 16 verbunden, der zwischen Arbeitskolben 2, Gehäuse 1 und Kolbenstange 3 gebildet ist. In den Leitungsabschnitten einmal zum Ringraum 16 als auch zum Speicherraum 5 sind Steuerventile 17 angeordnet, die jeweils zum Speicherraum 5 bzw. Ringraum 16 hin einen freien Durchfluß gewährleisten, hingegen in umgekehrter Richtung den Durchstrom drosseln, wobei diese Drosselung einstellbar ist. Während der Strom zu diesen Räumen dem Rückhublauf der Einrichtung dient, tritt die Drosselwirkung beim Eilgang bzw. Arbeitshub des Druckübersetzers auf.In the embodiment shown in FIG. 1, a drive spindle 9 is attached to the storage piston 7 in the axial line with the plunger 8, which drives through a linear motor 11, which is arranged outside the housing 1 and is fastened to it. As soon as the piston rod 3 has completed the rapid stroke and the plunger 8 is immersed in the control bore 6, the stroke of this plunger 8 is continued via the linear motor to generate a high pressure in the working space 4 and a corresponding advance of the piston rod 3. It is coaxial with the drive spindle 9 an annular piston 12 is axially displaceably arranged on the latter, which is loaded by a spring 13 and which on the side facing away from the spring 13 delimits an equalizing space 14 which on the other hand is delimited by the storage piston 7. This compensation space 14 is connected via a line 15 both to the storage space 5 and to an annular space 16, which is formed between the working piston 2, the housing 1 and the piston rod 3. Control valves 17 are arranged in the line sections once to the annular space 16 and to the storage space 5, each of which has a free flow to the storage space 5 and the annular space 16 ensure, however, throttle the flow in the opposite direction, this throttling is adjustable. While the current to these rooms serves the return stroke of the device, the throttling effect occurs during the rapid traverse or working stroke of the pressure intensifier.
Bei dem in Fig. 2 nur sehr vereinfacht dargestellten Ausführungsbeispiel ist auch die Kolbenstange 3 über einen nur prinzipiell dargestellten Spindeltrieb 18 betätigbar, der insbesondere als Linearmotor ausgebildet ist. Außerdem sind in Fig. 2 ein Servomotor 19, ein zusätzlicher Speicher 21 für Hydraulikflüssigkeit und ein Assynchronmotor 22 entnehmbar, welcher einen Spindeltrieb 23 der Spindel 24 betätigt, die wiederum achsgleich mit dem Tauchkolben 8 verbunden ist.In the embodiment shown only in a very simplified form in FIG. 2, the piston rod 3 can also be actuated via a spindle drive 18 which is only shown in principle and which is designed in particular as a linear motor. In addition, a servo motor 19, an additional accumulator 21 for hydraulic fluid and an asynchronous motor 22 can be removed in FIG. 2, which actuates a spindle drive 23 of the spindle 24, which in turn is connected to the plunger 8 with the same axis.
Alle in der Beschreibung, den nachfolgenden Ansprüchen und der Zeichnung dargestellten Merkmale können sowohl einzeln als auch in beliebiger Kombination miteinander erfindungswesentlich sein. All the features shown in the description, the following claims and the drawing can be essential to the invention both individually and in any combination with one another.
BezugszahlenlisteLIST OF REFERENCE NUMBERS
1 Gehäuse1 housing
2 Arbeitskolben2 working pistons
3 Kolbenstange3 piston rod
4 Arbeitsraum4 work space
5 Speicherraum5 storage space
6 Steuerbohrung6 control bore
7 Speicherkolben7 accumulator pistons
8 Tauchkolben8 plungers
9 Antriebsspindel9 drive spindle
1010
1 1 Linearmotor1 1 linear motor
12 Ringkolben12 ring pistons
13 Feder13 spring
14 Ausgleichsraum14 compensation room
15 Leitung15 line
16 Ringraum16 annulus
17 Steuerventil17 control valve
18 Spindeltrieb18 spindle drive
19 Servomotor19 servo motor
2020
21 Speicher21 memory
22 Motor22 engine
23 Spindeltrieb23 spindle drive
24 Spindel 24 spindle

Claims

Hydraulischer DruckübersetzerAnsprüche Hydraulic pressure intensifier claims
1. Hydraulischer Druckübersetzer1. Hydraulic pressure intensifier
-mit einem in einem Aggregatsgehäuse (1) angeordneten-with one arranged in a unit housing (1)
Arbeitsraum (4) für wechselnde Drücke, nämlich einem niederenWork space (4) for changing pressures, namely a low one
Speicherdruck für einen Eilgangvorlauf und einem Rückhub sowie einem hohen Arbeitsdruck für einen Arbeitshub,Accumulator pressure for a rapid traverse and a return stroke as well as a high working pressure for a working stroke,
-mit einem den Arbeitsraum (4) stirnseitig begrenzenden und durch den Arbeitsdruck im Arbeitsgehäuse (1) für den Arbeitshub betätigbaren Arbeitskolben (2), welcher durch eine Kolbenstange (3) nach außerhalb des Gehäuses (1) geführt ist,with a working piston (2) which delimits the working space (4) at the end and can be actuated by the working pressure in the working housing (1) for the working stroke, which is guided through a piston rod (3) to the outside of the housing (1),
-mit einem mit dem Arbeitsraum (4) hydraulisch verbindbaren, in einem Zylinderraum des Gehäuses (1) angeordneten Speicherraum (5), aus dem während des Eilgangs Hydrauliköl unter Speicherdruck in den Arbeitsraum (4) strömt und beim Rückhub wieder zurück strömt, -mit einem als Hochdruckerzeuger betätigbaren nach dem Eilgang in den Arbeitsraum (4) tauchenden, eine Antriebsspindel (9) aufweisenden Tauchkolben (8) undwith a storage space (5) which can be hydraulically connected to the working space (4) and is arranged in a cylinder space of the housing (1), from which hydraulic oil flows into the working space (4) under storage pressure during the rapid traverse and flows back again on the return stroke, -with a plunger (8) which can be actuated after the rapid traverse into the working space (4) and has a drive spindle (9) and can be actuated as a high pressure generator
-mit einem Antrieb des Tauchkolbens (8) auf der der Arbeitsraum (4) abgewandten Seite für den Eilgang als auch den Arbeitshub zur-with a drive of the plunger (8) on the side facing away from the working space (4) for the rapid traverse as well as the working stroke
Erzeugung des hohen Arbeitsdrucks dadurch gekennzeichnet, dass der Tauchkolben (8), bzw. die Antriebsspindel (9) mindestens für den Arbeitshub durch elektrische Arbeitsmittel ( 1 1 , 18, 22, 23) angetrieben wird.Generation of the high working pressure, characterized in that the plunger (8) or the drive spindle (9) is driven at least for the working stroke by electrical working means (11, 18, 22, 23).
2. Druckübersetzer nach Anspruch 1 , dadurch gekennzeichnet, dass als Antriebsmittel ein Elektromotor (11, 18, 22) dient.2. Pressure intensifier according to claim 1, characterized in that an electric motor (11, 18, 22) serves as drive means.
3. Druckübersetzer nach Anspruch 2, dadurch gekennzeichnet, dass als elektrisches Antriebsmittel ein Kugelspindelmotor odgl. dient.3. Pressure intensifier according to claim 2, characterized in that a ball screw motor or the like as the electrical drive means. serves.
4. Druckübersetzer nach Anspruch 2, dadurch gekennzeichnet, dass der Elektromotor als Linearmotor (1 1) ausgebildet ist, bei dem der Anker mindestens mittelbar mit dem Tauchkolben (8) und/ oder der Kolbenstange (3) des Arbeitskolbens (2) verbunden ist.4. Pressure intensifier according to claim 2, characterized in that the electric motor is designed as a linear motor (1 1), in which the armature is at least indirectly connected to the plunger (8) and / or the piston rod (3) of the working piston (2).
5. Druckübersetzer nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der vor dem Arbeitshub liegende Eilganghub und/ oder der nach dem Arbeitshub liegende Rückhub mindestens teilweise hydraulisch bewirkt wird.5. Pressure intensifier according to one of the preceding claims, characterized in that the rapid traverse stroke lying before the working stroke and / or the return stroke lying after the working stroke is at least partially effected hydraulically.
6. Druckübersetzer nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass innerhalb des Gehäuses (1) und um die Kolbenstange (3), sowie begrenzt durch den Arbeitskolben (2), ein Ringraum (16) zur hydraulischen Steuerung, insbesondere für den Rückhub vorhanden ist. 6. Pressure intensifier according to one of the preceding claims, characterized in that an annular space (16) for hydraulic control, in particular for the return stroke, is present within the housing (1) and around the piston rod (3) and also delimited by the working piston (2) is.
7. Druckübersetzer nach Anspruch 6, dadurch gekennzeichnet, dass zwischen Ringraum (16) und Speicherraum (5) eine hydraulische Verbindung (15) besteht.7. Pressure intensifier according to claim 6, characterized in that there is a hydraulic connection (15) between the annular space (16) and the storage space (5).
8. Druckübersetzer nach Anspruch 7, dadurch gekennzeichnet, dass um die Antriebsspindel (9) ein zur Antriebsspindel und zum Gehäuse ( 1) hin abgedichteter Ringkolben (12) axial verschiebbar angeordnet ist, welcher einen, mit Hydraulikflüssigkeit gefüllten, Ausgleichsraum (14) zum Speicherkolben (7) hin begrenzt und welcher auf der dem Speicherkolben (7) abgewandten Seite durch eine den Hydraulikniederdruck bestimmenden Feder (13) belastet ist, und welcher mit der hydraulischen Verbindung ( 15) verbunden ist.8. Pressure intensifier according to claim 7, characterized in that around the drive spindle (9) to the drive spindle and to the housing (1) sealed annular piston (12) is arranged axially displaceably, which, filled with hydraulic fluid, compensation chamber (14) to the storage piston (7) and which is loaded on the side facing away from the accumulator piston (7) by a spring (13) determining the hydraulic low pressure, and which is connected to the hydraulic connection (15).
9. Druckübersetzer nach Anspruch 8 oder 9, dadurch gekennzeichnet, dass in der hydraulischen Verbindung zwischen Speicherraum (5) und Ringraum (16), bzw. Ausgleichsraum (14) jeweils ein Steuerventil (17) angeordnet ist, welches als Einwegventil in Strömungsrichtung aus Ringraum (16) oder Speicherraum (5) sperrt, hingegen in Strömungsrichtung zu diesen Räumen drosselt.9. Pressure intensifier according to claim 8 or 9, characterized in that in the hydraulic connection between the storage space (5) and the annular space (16), or compensation space (14), a control valve (17) is arranged, which as a one-way valve in the flow direction from the annular space (16) or storage space (5) blocks, but throttles in the direction of flow to these spaces.
10. Druckübersetzer nach einem der Ansprüche 4 bis 10, dadurch gekennzeichnet, dass die Antriebsspindel (9), bzw. die Kolbenstange (3) durch einen Linearmotor antreibbar ist. 10. Pressure intensifier according to one of claims 4 to 10, characterized in that the drive spindle (9) or the piston rod (3) can be driven by a linear motor.
EP01940104A 2000-03-27 2001-03-26 Hydraulic pressure intensifier Expired - Lifetime EP1269026B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10014763 2000-03-27
DE10014763 2000-03-27
PCT/DE2001/001205 WO2001073298A2 (en) 2000-03-27 2001-03-26 Hydraulic pressure intensifier

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EP1269026A2 true EP1269026A2 (en) 2003-01-02
EP1269026B1 EP1269026B1 (en) 2003-11-12

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US (1) US20040028543A1 (en)
EP (1) EP1269026B1 (en)
JP (1) JP2004503702A (en)
CN (1) CN1427924A (en)
AU (1) AU7381801A (en)
DE (3) DE10191171D2 (en)
WO (1) WO2001073298A2 (en)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003102428A1 (en) * 2002-05-31 2003-12-11 Tox Pressotechnik Gmbh & Co. Kg Method for switching a hydraulic pressure intensifier
AU2003255126A1 (en) * 2003-05-13 2004-12-03 Ju Jiao A hydraulic intensifier electromotion cylinder
US20050091972A1 (en) * 2003-10-31 2005-05-05 Redman Kenneth K. Electrohydraulic actuator
EP1724043A1 (en) * 2005-05-18 2006-11-22 Gerd Friedrich Guenter Dr. Koennecker Hydraulic shears or similar tools with a piston driven by a linear electric motor
US8695414B2 (en) 2011-07-12 2014-04-15 Halliburton Energy Services, Inc. High pressure and flow rate pump useful in formation fluid sample testing
TWM423162U (en) * 2011-10-21 2012-02-21 Chanto Air Hydraulics Co Ltd Pressure boosting cylinder with separated oil and gas
TWM423163U (en) * 2011-10-21 2012-02-21 Chanto Air Hydraulics Co Ltd Pressure boosting cylinder with invisible loop
DE102012008902A1 (en) * 2012-05-08 2013-11-14 Tox Pressotechnik Gmbh & Co. Kg Hydropneumatic device for pressure transmission and riveting device
CN102691636B (en) * 2012-06-09 2015-02-25 林志元 Water continuous pressurizing device
CN102913509A (en) * 2012-11-23 2013-02-06 湖北汽车工业学院 Electrohydraulic pressurizing cylinder and pressing machine equipment with same
CN103185046B (en) * 2013-03-14 2016-06-29 西安交通大学 A kind of AC servo direct-drive supercharged formula band oil tank electric hydraulic cylinder and boosting method thereof
CN105736796B (en) * 2016-03-30 2018-09-21 太原理工大学 A kind of electromechanical linkage fluid control valve driver
CN106050760B (en) * 2016-06-27 2018-12-18 武汉仁达秦雕数控设备有限公司 Four piston air water pressurized cylinders
CN112196844B (en) * 2020-09-27 2021-11-05 张家口长城液压油缸有限公司 High-pressure high-purity energy accumulator for hydraulic system

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2625884A1 (en) * 1976-06-09 1977-12-15 Transform Verstaerkungsmasch PROCESS AND DEVICE FOR HYDROPNEUMATICALLY GENERATING A PRESSURE OR. PRESS FORCE
DE4026959A1 (en) * 1990-08-25 1992-02-27 Illig Maschinenbau Adolf Electrically driven unit with thrust rod - moves in cylindrical pipe with spindle, cover, hole and piston
DE4223411A1 (en) * 1992-07-02 1994-01-05 Pressotechnik Pressen Und Werk Hydropneumatic pressure intensifier
JP2955220B2 (en) * 1995-12-06 1999-10-04 太陽鉄工株式会社 In-line pressure booster
JP3331152B2 (en) * 1997-07-29 2002-10-07 東芝機械株式会社 Closed hydraulic pressure booster

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO0173298A2 *

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JP2004503702A (en) 2004-02-05
EP1269026B1 (en) 2003-11-12
DE50100964D1 (en) 2003-12-18
US20040028543A1 (en) 2004-02-12
CN1427924A (en) 2003-07-02
AU7381801A (en) 2001-10-08
DE10191171D2 (en) 2003-04-24
WO2001073298A2 (en) 2001-10-04
WO2001073298A3 (en) 2002-03-07
DE10115634A1 (en) 2002-01-24

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