EP0783395B1 - Hydraulic drive unit - Google Patents

Hydraulic drive unit Download PDF

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Publication number
EP0783395B1
EP0783395B1 EP94924302A EP94924302A EP0783395B1 EP 0783395 B1 EP0783395 B1 EP 0783395B1 EP 94924302 A EP94924302 A EP 94924302A EP 94924302 A EP94924302 A EP 94924302A EP 0783395 B1 EP0783395 B1 EP 0783395B1
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EP
European Patent Office
Prior art keywords
hydraulic
tool according
pressure pump
hydraulic tool
annular
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
EP94924302A
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German (de)
French (fr)
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EP0783395A1 (en
Inventor
Heinz Schwaiger
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.)
Weber-Hydraulik GmbH
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Weber Hydraulik GmbH Austria
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Publication of EP0783395A1 publication Critical patent/EP0783395A1/en
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/005—Hydraulic driving means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/0008—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators
    • F04B11/0033—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using accumulators with a mechanical spring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/02—Stopping, starting, unloading or idling control
    • F04B49/03—Stopping, starting, unloading or idling control by means of valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2205/00—Fluid parameters
    • F04B2205/16—Opening or closing of a valve in a circuit

Definitions

  • the present invention relates to a hydraulic tool according to the preamble of claim 1.
  • Such a hydraulic tool is from the previously published (same applicant) German utility model DE-U-92 03 270 known.
  • a tool 8 by means of a Power transmission device 25 on a working piston 24 a working cylinder 3 attached.
  • This tool 8 forms part of the whole, portable and very mobile Hydraulic tool, which by the operator on two Handles 5 and 6 held and operated via a switch 7 can be.
  • a Hydraulic circuit control valve assembly (not shown) controlled to operate the working cylinder 3.
  • the pressure of a hydraulic fluid used in the hydraulic circuit is generated by the hydraulic high pressure pump 2, which is driven by an electric motor 1, which an electrical connection 9 receives its power supply.
  • the hydraulic high-pressure pump 2 comprises a swash plate 18, which is supported by an angular contact ball bearing 26 and by means of pistons 10 that entering through an inflow opening 13 Hydraulic fluid compressed and via check valves 12 feeds a collecting duct 15.
  • the hydraulic fluid will the working piston 24 via a feed bore (not shown) supplied or discharged via a return bore 29.
  • the ring buffer 19 is in the case of DE-U-92 03 270 Working cylinder 3 arranged around; he is seen axially spaced from the hydraulic high-pressure pump 2 and over corresponding connecting lines or holes on the Hydraulic circuit connected.
  • the number of sealing points is relatively high in this arrangement.
  • US-A-2 444 550 is a hydraulic drive unit for a closed hydraulic circuit with one Hydraulic high pressure pump and an expansion tank for a hydraulic fluid is known.
  • the expansion tank of this Drive unit is designed as a pressure accumulator and surrounds the hydraulic high-pressure pump is essentially cylindrical in shape.
  • the pressure accumulator stands over connecting holes with the inside of the hydraulic high pressure pump and has a variable volume. For controlling a control device is provided for the drive unit.
  • the ring buffer is in the form of a cylinder jacket arranged around the hydraulic high pressure pump and forms an integral unit with it. This eliminates longer connecting lines and the associated Sealing points.
  • the hydraulic drive unit according to the invention is very compactly built and has only one connection to the outside for the (electric) drive (right in Fig. 1) or the hydraulic output (left in Fig. 2). Otherwise the hydraulic drive unit forms a closed one Unit, the manufacture of which also simplifies is.
  • the energy supply can via the public power grid, via a portable Power generator or also ensured by a battery will.
  • the hydraulic high-pressure pump is designated by 102 from the electric motor 101 directly or via a transmission (not shown) is driven.
  • the hydraulic high pressure pump 102 is described below with reference to FIG. 2 described in more detail.
  • a ring buffer 119 is arranged around it, which essentially has the shape of a cylinder jacket.
  • an annular piston 120 Within the Ring memory 119 is an annular piston 120, the is essentially L-shaped, the longer one Leg runs in the axial direction and radially facing inward has a recess that one Annulus 134 forms that in the right dead center position (Fig. 1) of the annular piston 120 over two radially extending Connection bores 132 and 133 with the interior of the hydraulic high-pressure pump 102 communicates.
  • the ring piston 120 is opposite the exterior of the hydraulic high pressure pump 102 provided with a seal 135; the shorter one Leg of the annular piston 120 extends radially Direction and is equipped with a seal 136 which seals the ring buffer 119 to the outer jacket.
  • a spring 137 is arranged, the Ring piston 120 loaded and pushes to the right in Fig. 1.
  • the hydraulic drive unit forms a compact unit, at the one end (right in Fig. 1) the drive is required via the electric motor 101 and at the output at the other end (left in Fig. 1) two feed lines 139 (Fig. 2).
  • the hydraulic drive unit is via the switch 107, which in turn actuated the control slide 140 by means of the control rocker 131, controlled.
  • a microswitch 122 is provided for switching the electric motor on and off 101. Since the Ring buffer 119 "in" the hydraulic high-pressure pump 102 is integrated and not around the working cylinder as before arranged around is a much more compact Design possible.
  • the hydraulic high-pressure pump 102 is shown in FIG. 2.
  • the hydraulic high-pressure pump 102 is driven by means of the swash plate 118 with a constant angle of attack, which the pistons 110 back and forth in the cylinders moved here.
  • the swash plate 118 is in turn over the electric motor 101 driven, between the swash plate 118 and electric motor 101 for storage purposes Rolling bearings, preferably an angular contact ball bearing 126 is.
  • the pistons 110 form together with the cylinders at the end facing away from the swash plate 118, compression chambers 111, the discharge openings of check valves 112 are closable.
  • the cylinders are preferably made of hard metal; this has the advantage that at very high pressures, the expansion of the cylinder bores is relatively small.
  • the pressure generated by the hydraulic high pressure pump 102 is fed to a collecting channel 115 which is between the hydraulic high pressure pump 102 and the working cylinder (not shown).
  • the rear handle 105 is the electric motor 101 can be controlled via the switch 122 (FIG. 1), and on the other hand, by means of the control slide 140 Hydraulic fluid via the two feed lines 139 to the Working cylinder is fed or discharged.
  • Switching the electric motor 101 on and off via the Switch 122 is only in the end positions of the control spool 140 possible. With this forced mechanical coupling it is ensured that the electric motor 101 or the hydraulic high pressure pump 102 not against the closed Control spool 140 can run.
  • connection bores 132 and 133 to the ring buffer 119 takes place inside the hydraulic high pressure pump 102 pressure equalization instead of leads to a lower load on the seals 138.
  • FIG. 3 shows part of the hydraulic drive unit on average, with the control spool 140 set so is that the hydraulic fluid passes through the center of the two Supply lines 139 can flow; there is also a filling valve 116, which is shown when filling the Hydraulic circuit with hydraulic oil is used.
  • a filling valve 116 which is shown when filling the Hydraulic circuit with hydraulic oil is used.
  • reference number 117 is an adjustable pressure relief valve designated; this protects the drive unit from overload and allows the pressure in the hydraulic circuit adapted for different uses, limit.
  • a pressure gauge can be connected to port 114 will.

Abstract

A hydraulic drive unit is disclosed, in particular for a portable hydraulic tool. The hydraulic high-pressure pump (102) of the proposed unit is arranged inside a ring reservoir (119), thus making for a compact design which results in short fluid paths between the ring reservoir (119) and the hydraulic high-pressure pump (102) and reduces the number of sealing points.

Description

Die vorliegende Erfindung betrifft ein Hydraulik-Werkzeug gemäß dem Oberbegriff des Patentanspruchs 1.The present invention relates to a hydraulic tool according to the preamble of claim 1.

Ein derartiges Hydraulik-Werkzeug ist aus dem vorveröffentlichten (gleicher Anmelder) Deutschen Gebrauchsmuster DE-U-92 03 270 bekannt. Dort ist, wie in Fig. 4 der vorliegenden Anmeldung gezeigt, ein Werkzeug 8 mittels einer Kraftübertragungseinrichtung 25 an einem Arbeitskolben 24 eines Arbeitszylinders 3 angebracht. Dieses Werkzeug 8 bildet einen Teil des gesamten, tragbaren und sehr mobilen Hydraulik-Werkzeugs, welches von der Bedienperson an zwei Handgriffen 5 und 6 gehalten und über einen Schalter 7 betätigt werden kann. Mittels des Schalters 7 wird über eine (nicht gezeigte) Steuerventilanordnung der Hydraulik-Kreislauf zum Betrieb des Arbeitszylinders 3 angesteuert. Der im Hydraulik-Kreislauf benutzte Druck eines Hydraulikfluids wird durch die Hydraulik-Hochdruckpumpe 2 erzeugt, die von einem Elektromotor 1 angetrieben wird, der über einen elektrischen Anschluß 9 seine Stromversorgung erhält. Die Hydraulik-Hochdruckpumpe 2 umfaßt eine Taumelscheibe 18, die über ein Schrägkugellager 26 abgestützt ist und die mittels Kolben 10 das durch eine Zuflußöffnung 13 eintretende Hydraulikfluid komprimiert und über Rückschlagventile 12 einem Sammelkanal 15 zuführt. Das Hydraulikfluid wird dem Arbeitskolben 24 über eine Vorlaufbohrung (nicht dargestellt) zugeführt bzw. über eine Rücklaufbohrung 29 abgeführt. Ein im Niederdruckteil der Hydraulikantriebseinheit angeordneter Ringspeicher 19, der sich um den Arbeitszylinder 3 herum erstreckt, dient dazu, das Hydraulikfluid im Ausgleich zu den Bewegungen des Arbeitskolbens 24 aufzunehmen, wobei ein Ringkolben 20 unter Federbelastung steht, um eine entsprechende Ausgleichbewegung zu ermöglichen.Such a hydraulic tool is from the previously published (same applicant) German utility model DE-U-92 03 270 known. There is, as in Fig. 4 of the present Application shown a tool 8 by means of a Power transmission device 25 on a working piston 24 a working cylinder 3 attached. This tool 8 forms part of the whole, portable and very mobile Hydraulic tool, which by the operator on two Handles 5 and 6 held and operated via a switch 7 can be. By means of the switch 7 is a Hydraulic circuit control valve assembly (not shown) controlled to operate the working cylinder 3. The pressure of a hydraulic fluid used in the hydraulic circuit is generated by the hydraulic high pressure pump 2, which is driven by an electric motor 1, which an electrical connection 9 receives its power supply. The hydraulic high-pressure pump 2 comprises a swash plate 18, which is supported by an angular contact ball bearing 26 and by means of pistons 10 that entering through an inflow opening 13 Hydraulic fluid compressed and via check valves 12 feeds a collecting duct 15. The hydraulic fluid will the working piston 24 via a feed bore (not shown) supplied or discharged via a return bore 29. One in the low pressure part of the hydraulic drive unit arranged ring memory 19, which is around the working cylinder 3 extends around, serves to the hydraulic fluid in To compensate for the movements of the working piston 24, an annular piston 20 is under spring load, to enable a corresponding compensatory movement.

Der Ringspeicher 19 ist im Falle der DE-U-92 03 270 um den Arbeitszylinder 3 herum angeordnet; er ist axial gesehen von der Hydraulik-Hochdruckpumpe 2 beabstandet und über entsprechende Verbindungsleitungen bzw. Bohrungen an den Hydraulik-Kreislauf angeschlossen. Die Anzahl der Dichtstellen ist bei dieser Anordnung relativ hoch.The ring buffer 19 is in the case of DE-U-92 03 270 Working cylinder 3 arranged around; he is seen axially spaced from the hydraulic high-pressure pump 2 and over corresponding connecting lines or holes on the Hydraulic circuit connected. The number of sealing points is relatively high in this arrangement.

Aus der US-A-2 444 550 ist eine Hydraulik-Antriebseinheit für einen geschlossenen Hydraulikkreislauf mit einer Hydraulik-Hochdruckpumpe und einem Ausgleichsbehälter für ein Hydraulikfluid bekannt. Der Ausgleichsbehälter dieser Antriebseinheit ist als Druckspeicher ausgebildet und umgibt die Hydraulik-Hochdruckpumpe im wesentlichen zylindermantelförmig. Der Druckspeicher steht über Verbindungsbohrungen mit dem Inneren der Hydraulik-Hochdruckpumpe in Verbindung und weist ein variables Volumen auf. Zur Steuerung der Antriebseinheit ist eine Steuereinrichtung vorgesehen.US-A-2 444 550 is a hydraulic drive unit for a closed hydraulic circuit with one Hydraulic high pressure pump and an expansion tank for a hydraulic fluid is known. The expansion tank of this Drive unit is designed as a pressure accumulator and surrounds the hydraulic high-pressure pump is essentially cylindrical in shape. The pressure accumulator stands over connecting holes with the inside of the hydraulic high pressure pump and has a variable volume. For controlling a control device is provided for the drive unit.

Es ist die Aufgabe der Erfindung, ein Hydraulik-Werkzeug gemäß Oberbegriff des Patentanspruchs 1 zu schaffen, bei dem die Fluidwege kürzer sind und die Anzahl der Dichtstellen reduziert ist.It is the object of the invention to provide a hydraulic tool to create according to the preamble of claim 1, where the fluid paths are shorter and the number of Sealing points is reduced.

Diese Aufgabe wird durch die im kennzeichnenden Teil des Patentanspruchs 1 angegebenen Merkmale gelöst.This task is carried out in the characterizing part of the Features specified claim 1 solved.

Erfindungsgemäß wird der Ringspeicher in Form eines Zylindermantels um die Hydraulik-Hochdruckpumpe herum angeordnet und bildet mit dieser eine Integraleinheit. Dadurch entfallen längere Verbindungsleitungen und die damit verbundenen Dichtstellen. According to the invention, the ring buffer is in the form of a cylinder jacket arranged around the hydraulic high pressure pump and forms an integral unit with it. This eliminates longer connecting lines and the associated Sealing points.

Die erfindungsgemäße Hydraulik-Antriebseinheit ist sehr kompakt gebaut und hat nach Außen hin lediglich einen Anschluß für den (elektrischen) Antrieb (rechts in Fig. 1) bzw. den hydraulischen Abtrieb (links in Fig. 2). Ansonsten bildet die Hydraulik-Antriebseinheit eine abgeschlossene Baueinheit, deren Fertigung dadurch auch vereinfacht ist.The hydraulic drive unit according to the invention is very compactly built and has only one connection to the outside for the (electric) drive (right in Fig. 1) or the hydraulic output (left in Fig. 2). Otherwise the hydraulic drive unit forms a closed one Unit, the manufacture of which also simplifies is.

Da die Fluidwege zwischen dem Ringspeicher und den Steuerkanten der Steuereinrichtung insgesamt kürzer und weniger kompliziert aufgebaut sind, ist einerseits das Entlüften einfacher durchzuführen und andererseits die hydraulische Steuerung exakter.Because the fluid paths between the ring buffer and the control edges the control device overall shorter and less venting is complicated easier to do and hydraulic Control more precise.

Weitere vorteilhafte Ausführungsformen und Merkmale ergeben sich aus den Unteransprüchen.Further advantageous embodiments and features result itself from the subclaims.

Die Erfindung wird im folgenden anhand der Zeichnungen, die ein Ausführungsbeispiel zeigen, ausführlich dargestellt. Es zeigen:

  • Fig. 1 im linken Teil der Figur eine teilweise aufgebrochene Schnittdarstellung eines Teils des Hydraulik-Werkzeugs, der im wesentlichen die Antriebseinheit umfaßt; im rechten Teil der Figur 1 eine teilweise Schnittdarstellung entlang der Linie A-A;
  • Fig. 2 eine Schnittansicht der Hydraulik-Hochdruckpumpe;
  • Fig. 3 eine Schnittansicht entlang der Linie B-B in Figur 2;
  • Fig. 4 eine Schnittdarstellung eines Hydraulik-Werkzeugs nach der G 92 03 270.2.
    • The invention is illustrated below with reference to the drawings which show an embodiment. Show it:
  • Figure 1 in the left part of the figure, a partially broken sectional view of a part of the hydraulic tool, which essentially comprises the drive unit. in the right part of Figure 1 is a partial sectional view along the line AA;
  • Fig. 2 is a sectional view of the hydraulic high pressure pump;
  • 3 shows a sectional view along the line BB in FIG. 2;
  • Fig. 4 is a sectional view of a hydraulic tool according to G 92 03 270.2.

    • Bezugnehmend auf die Figuren 1 bis 3 wird nun die Erfindung anhand eines Ausführungsbeispiels erläutert, wobei die sich funktional entsprechenden Bauteile, die auch in Fig. 4 dargestellt sind, mit Bezugszeichen versehen sind, die gegenüber der Fig. 4 um 100 erhöht sind.Referring now to Figures 1 to 3, the invention explained using an exemplary embodiment, wherein the functionally corresponding components that are also in 4 are shown, are provided with reference numerals, which are increased by 100 compared to FIG. 4.

    In Fig. 1 ist einer der beiden Handgriffe 105 gezeigt, sowie der Schalter 107 zur Bedienung des Hydraulik-Werkzeuges. Am rechten Ende des Hydraulik-Werkzeugs ist der elektrische Anschluß 109 vorgesehen, der den Elektromotor 101 mit Energie versorgt. Die Energieversorgung kann dabei über das öffentliche Stromnetz, über einen transportablen Stromgenerator oder auch über einen Akku sichergestellt werden.1 shows one of the two handles 105, and the switch 107 for operating the hydraulic tool. At the right end of the hydraulic tool is the electrical connection 109 provided of the electric motor 101 powered. The energy supply can via the public power grid, via a portable Power generator or also ensured by a battery will.

    Mit 102 ist die Hydraulik-Hochdruckpumpe bezeichnet, die vom Elektromotor 101 direkt oder aber über ein Getriebe (nicht dargestellt) angetrieben wird. Die Hydraulik-Hochdruckpumpe 102 wird weiter unten, mit Bezug zur Fig. 2 näher beschrieben. Um die Hydraulik-Hochdruckpumpe 102 herum ist ein Ringspeicher 119 angeordnet, der im wesentlichen die Form eines Zylindermantels hat. Innerhalb des Ringspeichers 119 befindet sich ein Ringkolben 120, der im wesentlichen L-förmig ausgebildet ist, wobei der längere Schenkel in axialer Richtung verläuft und radial einwärts zeigend eine Aussparung aufweist, die einen Ringraum 134 bildet, der in der rechten Totpunktlage (Fig. 1) des Ringkolbens 120 über zwei radial verlaufende Verbindungs-Bohrungen 132 und 133 mit dem Inneren der Hydraulik-Hochdruckpumpe 102 in Verbindung steht. Der Ringkolben 120 ist gegenüber dem Äußeren der Hydraulik-Hochdruckpumpe 102 mit einer Dichtung 135 versehen; der kürzere Schenkel des Ringkolbens 120 verläuft in radialer Richtung und ist mit einer Dichtung 136 ausgestattet, die den Ringspeicher 119 zum Außenmantel hin abdichtet. Im Ringspeicher 119 ist eine Feder 137 angeordnet, die den Ringkolben 120 belastet und in Fig. 1 nach rechts drückt.The hydraulic high-pressure pump is designated by 102 from the electric motor 101 directly or via a transmission (not shown) is driven. The hydraulic high pressure pump 102 is described below with reference to FIG. 2 described in more detail. To the hydraulic high pressure pump 102 a ring buffer 119 is arranged around it, which essentially has the shape of a cylinder jacket. Within the Ring memory 119 is an annular piston 120, the is essentially L-shaped, the longer one Leg runs in the axial direction and radially facing inward has a recess that one Annulus 134 forms that in the right dead center position (Fig. 1) of the annular piston 120 over two radially extending Connection bores 132 and 133 with the interior of the hydraulic high-pressure pump 102 communicates. The ring piston 120 is opposite the exterior of the hydraulic high pressure pump 102 provided with a seal 135; the shorter one Leg of the annular piston 120 extends radially Direction and is equipped with a seal 136 which seals the ring buffer 119 to the outer jacket. in the Ring memory 119, a spring 137 is arranged, the Ring piston 120 loaded and pushes to the right in Fig. 1.

    Die Hydraulik-Antriebseinheit bildet eine kompakte Baueinheit, bei der am einen Ende (rechts in Fig. 1) der Antrieb über den Elektromotor 101 erforderlich ist und bei der am anderen Ende (links in Fig. 1) der Abtrieb über zwei Zuführleitungen 139 (Fig. 2) erfolgt. Die Hydraulik-Antriebseinheit wird über den Schalter 107, der wiederum mittels der Steuerwippe 131 den Steuerschieber 140 betätigt, angesteuert. Zum Ein- und Ausschalten des Elektromotors 101 ist ein Mikroschalter 122 vorgesehen. Da der Ringspeicher 119 "in" die Hydraulik-Hochdruckpumpe 102 integriert ist und nicht wie vorher um den Arbeitszylinder herum angeordnet ist, ist eine wesentlich kompaktere Bauform möglich.The hydraulic drive unit forms a compact unit, at the one end (right in Fig. 1) the drive is required via the electric motor 101 and at the output at the other end (left in Fig. 1) two feed lines 139 (Fig. 2). The hydraulic drive unit is via the switch 107, which in turn actuated the control slide 140 by means of the control rocker 131, controlled. For switching the electric motor on and off 101, a microswitch 122 is provided. Since the Ring buffer 119 "in" the hydraulic high-pressure pump 102 is integrated and not around the working cylinder as before arranged around is a much more compact Design possible.

    In der Fig. 2 ist die Hydraulik-Hochdruckpumpe 102 dargestellt. Der Antrieb der Hydraulik-Hochdruckpumpe 102 erfolgt mittels der Taumelscheibe 118 mit konstantem Anstellwinkel, die die Kolben 110 in den Zylindern hin und her bewegt. Die Taumelscheibe 118 wird ihrerseits über den Elektromotor 101 angetrieben, wobei zwischen Taumelscheibe 118 und Elektromotor 101 zu Lagerungszwecken ein Wälzlager, vorzugsweise ein Schrägkugellager 126 angeordnet ist. Die Kolben 110 bilden zusammen mit den Zylindern am der Taumelscheibe 118 abgewandten Ende Verdichtungskammern 111, deren Ausstoßöffnungen von Rückschlagventilen 112 verschließbar sind. Vorzugsweise sind die Zylinder aus Hartmetall gefertigt; dies hat den Vorteil, daß bei den sehr hohen Drücken die Ausdehnung der Zylinderbohrungen relativ klein ist. The hydraulic high-pressure pump 102 is shown in FIG. 2. The hydraulic high-pressure pump 102 is driven by means of the swash plate 118 with a constant angle of attack, which the pistons 110 back and forth in the cylinders moved here. The swash plate 118 is in turn over the electric motor 101 driven, between the swash plate 118 and electric motor 101 for storage purposes Rolling bearings, preferably an angular contact ball bearing 126 is. The pistons 110 form together with the cylinders at the end facing away from the swash plate 118, compression chambers 111, the discharge openings of check valves 112 are closable. The cylinders are preferably made of hard metal; this has the advantage that at very high pressures, the expansion of the cylinder bores is relatively small.

    Der von der Hydraulik-Hochdruckpumpe 102 erzeugte Druck wird einem Sammelkanal 115 zugeleitet, der sich zwischen der Hydraulik-Hochdruckpumpe 102 und dem Arbeitszylinder (nicht dargestellt) befindet. Mittels des Schalters 107 am hinteren Handgriff 105 ist einerseits der Elektromotor 101 über den Schalter 122 (Fig. 1) ansteuerbar, sowie andererseits mittels des Steuerschiebers 140 das Hydraulikfluid über die beiden Zuführleitungen 139 dem Arbeitszylinder zugeführt bzw. abgeführt wird.The pressure generated by the hydraulic high pressure pump 102 is fed to a collecting channel 115 which is between the hydraulic high pressure pump 102 and the working cylinder (not shown). Using switch 107 on the one hand, the rear handle 105 is the electric motor 101 can be controlled via the switch 122 (FIG. 1), and on the other hand, by means of the control slide 140 Hydraulic fluid via the two feed lines 139 to the Working cylinder is fed or discharged.

    Das Ein- und Ausschalten des Elektromotors 101 über den Schalter 122 ist nur in den Endlagen des Steuerschiebers 140 möglich. Mit dieser zwangsweisen mechanischen Kopplung ist sichergestellt, daß der Elektromotor 101 bzw. die Hydraulik-Hochdruckpumpe 102 nicht gegen den geschlossenen Steuerschieber 140 laufen können.Switching the electric motor 101 on and off via the Switch 122 is only in the end positions of the control spool 140 possible. With this forced mechanical coupling it is ensured that the electric motor 101 or the hydraulic high pressure pump 102 not against the closed Control spool 140 can run.

    Durch die Verbindungsbohrungen 132 und 133 zum Ringspeicher 119 (Niederdruckseite) findet im Inneren der Hydraulik-Hochdruckpumpe 102 ein Druckausgleich statt, der zu einer geringeren Belastung der Dichtungen 138 führt.Through the connection bores 132 and 133 to the ring buffer 119 (low pressure side) takes place inside the hydraulic high pressure pump 102 pressure equalization instead of leads to a lower load on the seals 138.

    Die Fig. 3 zeigt einen Teil der Hydraulik-Antriebseinheit im Schnitt, wobei der Steuerschieber 140 so eingestellt ist, daß das Hydraulikfluid durch die mittige der beiden Zuführleitungen 139 strömen kann; weiterhin ist ein Füllventil 116 dargestellt, welches bei der Füllung des Hydraulik-Kreislaufes mit Hydraulik-Öl benutzt wird. Mit der Bezugszahl 117 ist ein einstellbares Überdruckventil bezeichnet; dieses schützt die Antriebseinheit vor Überlastung und erlaubt es, den Druck im Hydraulik-Kreislauf für verschiedene Verwendungszwecke angepaßt, zu begrenzen. Am Anschluß 114 kann ein Druckmeßgerät angeschlossen werden.3 shows part of the hydraulic drive unit on average, with the control spool 140 set so is that the hydraulic fluid passes through the center of the two Supply lines 139 can flow; there is also a filling valve 116, which is shown when filling the Hydraulic circuit with hydraulic oil is used. With reference number 117 is an adjustable pressure relief valve designated; this protects the drive unit from overload and allows the pressure in the hydraulic circuit adapted for different uses, limit. A pressure gauge can be connected to port 114 will.

    Claims (10)

    1. Hydraulic tool with closed hydraulic circuit in which an operational piston (24) is fed hydraulic fluid from an annular storage by a high-pressure pump (102), and the annular storage serves as a compensating container which receives the hydraulic fluid in compensation of the movements of the operational piston, characterised in that the annular storage (119) encases the high-pressure pump (102) in the form of a cylindrical casing, forming together with the pump an integral drive unit for the operational piston (24).
    2. Hydraulic tool according to Claim 1, characterised in that the volume in the annular storage (119) is variable against an annular piston (120) which is loaded by a spring (137).
    3. Hydraulic tool according to Claim 1 or 2, characterised in that the annular storage (119) is connected via radial connecting bores (132, 133) to the low-pressure section of the high-pressure pump (102).
    4. Hydraulic tool according to Claim 2 or 3, characterised in that the annular piston (120) is essentially of L-shaped design, and the longer shank extends in the axial direction and the shorter shank extends radially outward.
    5. Hydraulic tool according to Claim 4, characterised in that the longer shank has on its radially inner side a recess which establishes an annular space (134) which is in a dead-centre position of the annular piston (120) connected via the connecting bores (132, 133) to the interior of the high-pressure pump (102).
    6. Hydraulic tool according to Claim 4 or 5, characterised in that the longer shank is provided with a seal (135) placed radially and internally.
    7. Hydraulic tool according to one of Claims 4 to 6, characterised in that the shorter shank is provided with a seal (136) placed radially and externally.
    8. Hydraulic tool according to one of Claims 3 to 7, characterised in that the connecting bores (132, 133) attend to pressure compensation inside the high-pressure pump (102), thus relieving the seals (138) provided on the drive side.
    9. Hydraulic tool according to one of Claims 3 to 8, characterised in that the connecting bores (132, 133) are, axially seen, arranged on both sides of a roller bearing which is provided for mounting a tumbler disc (118) of the high-pressure pump (102).
    10. Hydraulic tool according to one of Claims 2 to 9, characterised in that the spring (137) is a helical spring.
    EP94924302A 1993-07-14 1994-07-29 Hydraulic drive unit Expired - Lifetime EP0783395B1 (en)

    Applications Claiming Priority (2)

    Application Number Priority Date Filing Date Title
    DE4323574A DE4323574C1 (en) 1993-07-14 1993-07-14 Hydraulic tool
    PCT/EP1994/002530 WO1996004107A1 (en) 1993-07-14 1994-07-29 Hydraulic drive unit

    Publications (2)

    Publication Number Publication Date
    EP0783395A1 EP0783395A1 (en) 1997-07-16
    EP0783395B1 true EP0783395B1 (en) 1998-09-30

    Family

    ID=6492777

    Family Applications (1)

    Application Number Title Priority Date Filing Date
    EP94924302A Expired - Lifetime EP0783395B1 (en) 1993-07-14 1994-07-29 Hydraulic drive unit

    Country Status (4)

    Country Link
    EP (1) EP0783395B1 (en)
    AT (1) ATE171661T1 (en)
    DE (2) DE4323574C1 (en)
    WO (1) WO1996004107A1 (en)

    Cited By (1)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    EP3638378B1 (en) 2017-06-12 2021-04-07 Weber-Hydraulik GmbH Hydraulic unit for hydraulic rescue tools, and equipped rescue tool

    Families Citing this family (4)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    DE29519941U1 (en) * 1995-12-15 1997-04-17 Wagner Paul Heinz Hydraulic pump unit
    DE19652691A1 (en) * 1996-12-18 1998-06-25 Roemheld A Gmbh & Co Kg Coupling and switching element for hydraulic tools
    DE29809935U1 (en) * 1998-06-03 1998-10-08 Heilmeier & Weinlein Hydraulic motor pump unit
    DE10028957C2 (en) 2000-06-16 2002-07-11 Lukas Hydraulik Gmbh & Co Kg Portable hydraulic pump unit

    Family Cites Families (7)

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    Publication number Priority date Publication date Assignee Title
    US2134237A (en) * 1936-11-10 1938-10-25 Saulnier Raymond Pump for aircraft machinery
    US2444550A (en) * 1944-05-20 1948-07-06 Electrol Inc Hydraulic power pack unit
    DE1223784B (en) * 1963-07-03 1966-09-01 Salzgitter Maschinen Ag Hammer drill
    US4094365A (en) * 1974-05-20 1978-06-13 Robert Bosch Gmbh Electrohydraulically operated portable power tool
    US4735048A (en) * 1986-10-24 1988-04-05 The Gregory Company Hydraulic tool
    DE9203270U1 (en) * 1992-03-11 1992-06-11 Hugo Junkers Werke Gmbh, 8000 Muenchen, De
    US5243761A (en) * 1992-03-18 1993-09-14 Hale Fire Pump Company Portable rescue tool

    Cited By (3)

    * Cited by examiner, † Cited by third party
    Publication number Priority date Publication date Assignee Title
    EP3638378B1 (en) 2017-06-12 2021-04-07 Weber-Hydraulik GmbH Hydraulic unit for hydraulic rescue tools, and equipped rescue tool
    US11273547B2 (en) 2017-06-12 2022-03-15 Weber-Hydraulik Gmbh Hydraulic unit for hydraulic rescue tools, and rescue tool equipped therewith
    US11738440B2 (en) 2017-06-12 2023-08-29 Weber-Hydraulik Gmbh Hydraulic unit for hydraulic rescue tools, and rescue tool equipped therewith

    Also Published As

    Publication number Publication date
    WO1996004107A1 (en) 1996-02-15
    DE4323574C1 (en) 1994-11-24
    EP0783395A1 (en) 1997-07-16
    DE59407023D1 (en) 1998-11-05
    ATE171661T1 (en) 1998-10-15

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