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EP1269026B1 - Hydraulic pressure intensifier - Google Patents

Hydraulic pressure intensifier Download PDF

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Publication number
EP1269026B1
EP1269026B1 EP01940104A EP01940104A EP1269026B1 EP 1269026 B1 EP1269026 B1 EP 1269026B1 EP 01940104 A EP01940104 A EP 01940104A EP 01940104 A EP01940104 A EP 01940104A EP 1269026 B1 EP1269026 B1 EP 1269026B1
Authority
EP
European Patent Office
Prior art keywords
piston
working
chamber
pressure
hydraulic
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP01940104A
Other languages
German (de)
French (fr)
Other versions
EP1269026A2 (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
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Publication of EP1269026A2 publication Critical patent/EP1269026A2/en
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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
    • F15B2211/21—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 genus of the main claim.
  • a hydraulic pressure intensifier of the generic type (DE-OS 42 23 411) the piston spindle is used to generate the high pressure of the plunger via a pneumatic drive piston actuated.
  • this pressure intensifier which in some Cases do not exist, or always with certain circumstances is connected and the use of the device by such Makes air supply dependent.
  • DE-OS-40 26 959 discloses an electric motor, via ball screw and corresponding nut driven linear unit with hydraulic Intensifier. However, this design is quite complex.
  • the hydraulic pressure intensifier according to the invention with the has characteristic features of the main claim in contrast, the advantage of simplifying the construction.
  • Lifting forces generated by electrical energy are sufficient for the to generate hydraulic high pressure.
  • the electrical energy in the generated electrical power is controlled, for example, by generating a lower force for the rapid traverse and when the plunger is immersed in the work area and due to the resulting higher pressure or mechanical process, an electrical switchover takes place. Also this is an additional advantage of the inventive solution.
  • Electric motor designed as a linear motor, in which the armature at least indirectly with or with the plunger connected drive spindle and / or the piston rod of the Working piston is connected, so that especially the rapid traverse through the linear forces can take place and where the drive spindle as Armature of the linear motor can serve.
  • Such linear motor on the piston rod can after immersion of the plunger in the working area on the linear motor Holding forces, due to the high pressure ratio, light be overcome, especially with rapid traverse and return stroke a quick adjustment is possible.
  • the rapid traverse before the working stroke and / or after the Return stroke lying at least partially hydraulic causes is provided.
  • the Invention is inside the housing and around the piston rod as well as an annular space bounded by the working piston hydraulic control available.
  • This enabled hydraulic servo function allows the use of known means, such as servo motor and the like.
  • the Invention is in the hydraulic connection between Storage space and annulus, or compensation space each one Control valve arranged, which towards the storage space (5) or annular space (16) guaranteed free flow, however in reverse Direction throttles the flow.
  • a housing 1 of a hydraulic pressure booster is over a working piston 2 a piston rod 3 driven and a hydraulic work space 4 is provided.
  • a Storage space 5 is provided, which with the work space 4 by a Control bore 6 is connected and by a storage piston 7 is limited.
  • a Plunger 8 Coaxial with the accumulator piston 7 is a Plunger 8 provided with a drive spindle 9 connected after a certain stroke in the control hole 6 dips, this locks and the continuation of the Hubes in the workspace 4 one according to the Diameter ratio of plunger 8 and working piston 2 given high pressure.
  • a power stroke via the plunger 8 is generated for machining the workpiece, for example one Punching the same.
  • Fig. 1 is with the Accumulator piston 7 in an axial line with the plunger 8 a Drive spindle 9 attached, which penetrates a linear motor 11, which is arranged outside of the housing 1 and attached to this is.
  • a linear motor 11 which is arranged outside of the housing 1 and attached to this is.
  • Coaxial to Drive spindle 9 is an annular piston 12 axially displaceable on this arranged, which is loaded by a spring 13 and on that delimits a compensation space 14 facing away from the spring 13, which on the other hand is limited by the accumulator piston 7.
  • This compensation space 14 is connected via a line 15 to both Storage space 5 and connected to an annular space 16, the formed between working piston 2, housing 1 and piston rod 3 is.
  • control valves 17 are arranged, each a free flow to the storage space 5 or the annular space 16 ensure, however, the flow in the opposite direction throttle, this throttling is adjustable.
  • Throttling effect during rapid traverse or working stroke of the pressure intensifier on.
  • FIG. 2 The embodiment is also the piston rod 3 only shown in principle operable spindle drive, the particular is designed as a linear motor.
  • Servo motor 19 and an additional reservoir 21 for hydraulic fluid removable.

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  • 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)

Description

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 23 411) 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 genus of the main claim. With a known hydraulic pressure intensifier of the generic type (DE-OS 42 23 411) the piston spindle is used to generate the high pressure of the plunger via a pneumatic drive piston actuated. As a result, there is a direct dependency on one pneumatic supply of this pressure intensifier, which in some Cases do not exist, or always with certain circumstances is connected and the use of the device by such Makes air supply dependent.

DE-OS-40 26 959 offenbart eine elektromotorisch, über Kugelrollspindel und entsprechende Mutter angetriebene Lineareinheit mit hydraulischen Druckübersetzer. Diese Bauweise ist aber ziemlich aufwendig.DE-OS-40 26 959 discloses an electric motor, via ball screw and corresponding nut driven linear unit with hydraulic Intensifier. However, this design is quite complex.

Die Erfindung und ihre VorteileThe invention and its advantages

Der erfindungsgemäße hydraulische Druckübersetzer mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, die Bauweise zu vereinfachen. 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. The hydraulic pressure intensifier according to the invention with the has characteristic features of the main claim in contrast, the advantage of simplifying the construction. Already small, Lifting forces generated by electrical energy are sufficient for the to generate hydraulic high pressure. Here is quite conceivable that the electrical energy in the generated electrical power is controlled, for example, by generating a lower force for the rapid traverse and when the plunger is immersed in the work area and due to the resulting higher pressure or mechanical process, an electrical switchover takes place. Also this is an additional advantage of the inventive solution.

Nach 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 Haltekräfte, aufgrund der hohen Druckübersetzung, leicht überwunden werden, wobei vor allem beim Eilgang und Rückhub eine schnelle Verstellung möglich ist.According to the invention Electric motor designed as a linear motor, in which the armature at least indirectly with or with the plunger connected drive spindle and / or the piston rod of the Working piston is connected, so that especially the rapid traverse through the linear forces can take place and where the drive spindle as Armature of the linear motor can serve. When using a Such linear motor on the piston rod can after immersion of the plunger in the working area on the linear motor Holding forces, due to the high pressure ratio, light be 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 after the Return stroke lying at least partially hydraulic causes.

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 is inside the housing and around the piston rod as well as an annular space bounded by the working piston hydraulic control available. This enabled hydraulic servo function allows the use of known means, such as servo motor 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 exists between the annulus and the storage space hydraulic connection.

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.After an additional configuration of the Invention is around the drive spindle to the drive spindle and ring piston sealed towards the housing axially displaceable arranged, which a, filled with hydraulic fluid, Compensation space limited to the storage piston and which on the side facing away from the accumulator piston by a Hydraulic low pressure determining spring is loaded, and which is connected to the hydraulic connection. This Compensation chamber 14 causes a uniform due to the spring Pressure in the storage space and in the annulus, 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 zum Speicherraum (5) bzw. Ringraum (16) hin einen freien Durchfluß gewährleistet, hingegen in umgekehrter Richtung den Durchstrom drosselt.According to an advantageous embodiment of the Invention is in the hydraulic connection between Storage space and annulus, or compensation space each one Control valve arranged, which towards the storage space (5) or annular space (16) guaranteed free flow, however in reverse Direction throttles the flow.

Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Beschreibung der Zeichnung und den Ansprüchen entnehmbar.Further advantages and advantageous configurations of the invention are the following description of the drawing and Removable 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. Show it:
  • Fig. 1 is a hydroelectric pressure intensifier in longitudinal section and
  • Fig. 2 greatly simplified a corresponding alternative example.

    • 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. The same in the two embodiments Components or components with the same function are listed below the same reference number.

    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.In a housing 1 of a hydraulic pressure booster is over a working piston 2 a piston rod 3 driven and a hydraulic work space 4 is provided. In addition, is a Storage space 5 is provided, which with the work space 4 by a Control bore 6 is connected and by a storage piston 7 is limited. Coaxial with the accumulator piston 7 is a Plunger 8 provided with a drive spindle 9 connected after a certain stroke in the control hole 6 dips, this locks and the continuation of the Hubes in the workspace 4 one according to the Diameter ratio of plunger 8 and working piston 2 given high pressure. During a first stroke, namely the rapid traverse, the piston rod 3 is on the workpiece moved up, then a power stroke via the plunger 8 is generated for machining the workpiece, for example one Punching the same.

    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 11 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 is with the Accumulator piston 7 in an axial line with the plunger 8 a Drive spindle 9 attached, which penetrates a linear motor 11, which is arranged outside of the housing 1 and attached to this is. 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 this plunger 8 continued via the linear motor for Generation of a high pressure in the work area 4 and one corresponding feed of the piston rod 3. Coaxial to Drive spindle 9 is an annular piston 12 axially displaceable on this arranged, which is loaded by a spring 13 and on that delimits a compensation space 14 facing away from the spring 13, which on the other hand is limited by the accumulator piston 7. This compensation space 14 is connected via a line 15 to both Storage space 5 and connected to an annular space 16, the formed between working piston 2, housing 1 and piston rod 3 is. In the line sections once to the annulus 16 as well to the storage space 5 control valves 17 are arranged, each a free flow to the storage space 5 or the annular space 16 ensure, however, the flow in the opposite direction throttle, this throttling is adjustable. During the stream serves the return stroke of the facility to these rooms, the occurs Throttling effect during rapid traverse or working stroke of the pressure intensifier on.

    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, und ein zusätzlicher Speicher 21 für Hydraulikflüssigkeit entnehmbar. In the case shown only in a very simplified manner in FIG. 2 The embodiment is also the piston rod 3 only shown in principle operable spindle drive, the particular is designed as a linear motor. In addition, in Fig. 2 Servo motor 19, and an additional reservoir 21 for hydraulic fluid removable.

    BezugszahlenlisteLIST OF REFERENCE NUMBERS

    11
    Gehäusecasing
    22
    Arbeitskolbenworking piston
    33
    Kolbenstangepiston rod
    44
    Arbeitsraumworking space
    55
    Speicherraumstorage space
    66
    Steuerbohrungcontrol bore
    77
    Speicherkolbenaccumulator piston
    88th
    Tauchkolbenplunger
    99
    Antriebsspindeldrive spindle
    10 1110 11
    Linearmotorlinear motor
    1212
    Ringkolbenannular piston
    1313
    Federfeather
    1414
    Ausgleichsraumcompensation space
    1515
    Leitungmanagement
    1616
    Ringraumannulus
    1717
    Steuerventilcontrol valve
    1818
    Spindeltriebspindle drive
    1919
    Servomotorservomotor
    20 2120 21
    SpeicherStorage
    2222
    Motorengine
    2323
    Spindeltriebspindle drive
    2424
    Spindelspindle

    Claims (5)

    1. Hydraulic pressure intensifier comprising
      an apparatus casing (1) having a working chamber (4) for accepting varying pressure, varying pressure including a low storage pressure for a rapid forward motion and a return stroke as well as a high working pressure for a working stroke;
      a working piston (2) delimiting an end face of working chamber (4), working piston (2) actuated by working pressure in casing (1) to effect a working stroke, working piston (2) being guided to the outside of the casing (1) by a piston rod (3);
      a storage chamber (5) connected hydraulically with working chamber (4) and disposed in a cylindrical chamber of the casing (1), wherein during the rapid forward motion and in response to storage pressure, hydraulic oil flows into working chamber (4) and wherein, during a return stroke, hydraulic oil flows back into storage chamber (5);
      a plunger piston (8) actuated as a high pressure generator, immersed within working chamber (4) after rapid forward motion and having a drive spindle (9); and
      a drive of plunger piston (8) on the side facing away from working chamber (4) for the rapid forward motion and for the working stroke for generating the high working pressure,
      characterised in that
      the plunger piston (8) or drive spindle (9) is driven by an electric linear motor (11, 18, 22, 23) at least for the working stroke and
      the armature of electric linear motor (11) is connected with plunger piston (8) and/or piston rod (3) of working piston (2).
    2. Pressure intensifier according to one of the previous claims, characterised in that within casing (1) and around piston rod (3) and delimited by working piston (2) there exists an annular chamber (16) for hydraulic control and in particular for the return stroke.
    3. Pressure intensifier according to claim 2, characterised in that a hydraulic connection (15) exists between annular chamber (16) and storage chamber (5).
    4. Pressure intensifier according to claim 3, characterised in that around drive spindle (9) is disposed in an axially displaceable fashion an annular piston (12) sealed from drive spindle and casing (1), annular piston (12) delimiting a compensating chamber (14) filled with hydraulic fluid from a storage piston (7), annular piston (12) stressed on the side facing away from storage piston (7) by a spring (13) determining the hydraulic low pressure, annular piston (12) connected with hydraulic connection (15).
    5. Pressure intensifier according to claim 4, characterised in that a control valve (17) is disposed in the hydraulic connection between storage chamber (5) and annular chamber (16) or compensating chamber (14) respectively, control valve (17) ensuring free passage towards storage chamber (5) or annular chamber (16) respectively, and in contrast restricting flow in the reverse direction.
    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

    Publications (2)

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

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    ID=7636269

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    Application Number Title Priority Date Filing Date
    EP01940104A Expired - Lifetime EP1269026B1 (en) 2000-03-27 2001-03-26 Hydraulic pressure intensifier

    Country Status (7)

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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) DE10115634A1 (en)
    WO (1) WO2001073298A2 (en)

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    US8695414B2 (en) 2011-07-12 2014-04-15 Halliburton Energy Services, Inc. High pressure and flow rate pump useful in formation fluid sample testing

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    AU2003245848A1 (en) * 2002-05-31 2003-12-19 Tox Pressotechnik Gmbh And 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
    TWM423163U (en) * 2011-10-21 2012-02-21 Chanto Air Hydraulics Co Ltd Pressure boosting cylinder with invisible loop
    TWM423162U (en) * 2011-10-21 2012-02-21 Chanto Air Hydraulics Co Ltd Pressure boosting cylinder with separated oil and gas
    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

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    JP2955220B2 (en) * 1995-12-06 1999-10-04 太陽鉄工株式会社 In-line pressure booster
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    Publication number Priority date Publication date Assignee Title
    US8695414B2 (en) 2011-07-12 2014-04-15 Halliburton Energy Services, Inc. High pressure and flow rate pump useful in formation fluid sample testing

    Also Published As

    Publication number Publication date
    DE50100964D1 (en) 2003-12-18
    US20040028543A1 (en) 2004-02-12
    DE10115634A1 (en) 2002-01-24
    JP2004503702A (en) 2004-02-05
    DE10191171D2 (en) 2003-04-24
    WO2001073298A3 (en) 2002-03-07
    WO2001073298A2 (en) 2001-10-04
    EP1269026A2 (en) 2003-01-02
    AU7381801A (en) 2001-10-08
    CN1427924A (en) 2003-07-02

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