DE19631804A1 - Hydraulic hoist with lifting cylinder driven by constant output pump - Google Patents

Hydraulic hoist with lifting cylinder driven by constant output pump

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Publication number
DE19631804A1
DE19631804A1 DE19631804A DE19631804A DE19631804A1 DE 19631804 A1 DE19631804 A1 DE 19631804A1 DE 19631804 A DE19631804 A DE 19631804A DE 19631804 A DE19631804 A DE 19631804A DE 19631804 A1 DE19631804 A1 DE 19631804A1
Authority
DE
Germany
Prior art keywords
lifting device
speed
pump
hydraulic lifting
constant pump
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
DE19631804A
Other languages
German (de)
Other versions
DE19631804B4 (en
Inventor
Joerg Dantlgraber
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.)
Bosch Rexroth AG
Original Assignee
Mannesmann Rexroth AG
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Publication date
Application filed by Mannesmann Rexroth AG filed Critical Mannesmann Rexroth AG
Priority to DE19631804A priority Critical patent/DE19631804B4/en
Publication of DE19631804A1 publication Critical patent/DE19631804A1/en
Application granted granted Critical
Publication of DE19631804B4 publication Critical patent/DE19631804B4/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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
    • 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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20569—Type of pump capable of working as pump and motor
    • 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
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41509—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41563—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • 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
    • F15B2211/7052—Single-acting output members

Landscapes

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

Abstract

The hoist cylinder receives fluid from a speed controlled electric motor which operates at a minimum speed to provide smooth working and adequate lubrication at very low lifting speeds by diverting excess fluid back to the fluid reservoir. The pump (1) is driven by a three-phase asynchronous motor (2) whose speed is controlled by a frequency converter (3) and electronic control unit (5). A two-way valve (7) directs hydraulic fluid from a reservoir tank (T) to the lifting cylinder (8) and to a by-pass (9) with adjustable throttle valve (10), controlled by the electronic control unit, so that lower pump delivery requirements cause greater flow to the tank.

Description

Die Erfindung betrifft eine hydraulische Hubeinrichtung, deren Hubzylinder die Arbeitsflüssigkeit von einer Konstantpumpe als Druckmittelquelle zugeführt bekommt. Die Konstantpumpe wird von einem drehzahlregelbaren Elektromotor angetrieben entsprechend der japanischen Offenlegungsschrift 5-186146 (A). Bei kleinen Hubgeschwindigkeiten mit entsprechend kleinen Pumpendrehzahlen ergibt sich bei Verwendung von Kolbenpumpen als Druckmittelquel­ le infolge auftretender Druckpulsation eine ungleichförmige Hub­ bewegung und mangelnde Schmierung der Kolben und Steuerflächen der Kolbenpumpe.The invention relates to a hydraulic lifting device, the Lift cylinder the working fluid from a constant pump as Pressure medium source is supplied. The constant pump is from a variable speed electric motor driven accordingly Japanese Laid-Open Publication 5-186146 (A). With small ones Stroke speeds with correspondingly low pump speeds results when using piston pumps as a pressure medium source le a non-uniform stroke due to pressure pulsation movement and insufficient lubrication of the pistons and control surfaces the piston pump.

Die Aufgabe der Erfindung besteht darin, die vorbezeichneten Mängel bei Verwendung von Konstantpumpen in Kolbenbauart als Druckmittelquelle für Hubeinrichtungen weitgehend zu unterbin­ den. Dies wird mit den kennzeichnenden Merkmalen des Anspruches 1 erzielt. Dadurch, daß ein Teil der von der Konstantpumpe ge­ lieferten Arbeitsflüssigkeitsmenge bei kleinen Pumpendrehzahlen zum Tank zurückführbar ist, muß auch bei kleinen Hubgeschwindig­ keiten des Hubzylinders die Pumpe mit einer höheren Drehzahl be­ trieben werden, die ausreicht, die vorgenannten Mängel weitge­ hend zu unterbinden.The object of the invention is that of the aforementioned Defects when using constant displacement pumps as piston To largely prevent pressure medium source for lifting devices the. This is with the characterizing features of the claim 1 scored. The fact that part of the ge of the constant pump delivered working fluid quantity at low pump speeds can be returned to the tank, even at small lifting speeds of the lifting cylinder, the pump runs at a higher speed are driven, which suffices, the aforementioned deficiencies to prevent.

Ein weiterer Vorteil der Erfindung ergibt sich dadurch, daß der die Pumpe antreibende Elektromotor nicht unter Last angefahren und damit ein unverhältnismäßig hoher Strom aus dem Netz gezogen werden muß.Another advantage of the invention results from the fact that the the electric motor driving the pump is not started under load and thus a disproportionately high amount of electricity is drawn from the grid must become.

Durch die japanische Offenlegungsschrift 6-183668 (A) vom 5.7.94 ist eine hydraulische Hubvorrichtung bekanntgeworden, an deren Druckleitung eine Bypass-Leitung angeschlossen ist, die über ein Schaltventil zum Tank führt. Diese Bypass-Leitung dient dazu, bei Inbetriebnahme der Anlage die zunächst noch zu kalte Ar­ beitsflüssigkeit solange unmittelbar zum Tank zurückzuführen, bis diese die vorgeschriebene Betriebstemperatur erreicht hat. Danach wird das betreffende Ventil geschlossen und der Hubbe­ trieb der Anlage aufgenommen.Japanese Patent Application 6-183668 (A) dated 5.7.94 has become known a hydraulic lifting device, at the A bypass line is connected via a pressure line Switch valve leads to the tank. This bypass line is used to when commissioning the system, the initially too cold ar as long as the liquid is returned directly to the tank,  until it has reached the prescribed operating temperature. Then the valve in question is closed and the stroke drive the system added.

Vorteilhafte Weiterbildungen der Erfindung ergeben sich aus den Unteransprüchen sowie der nachfolgenden Figurenbeschreibung ei­ nes Ausführungsbeispiels.Advantageous developments of the invention result from the Subclaims and the following figure description ei Nes embodiment.

Fig. 1 der Zeichnung veranschaulicht den schematischen Aufbau einer erfindungsgemäßen hydraulischen Hubeinrichtung und Fig. 1 of the drawing illustrates the schematic structure of a hydraulic lifting device and

Fig. 2 die Abhängigkeit der zum Tank zurückströmenden Teilmenge der Fördermenge der Pumpe in Abhängigkeit deren Drehzahl. Fig. 2 shows the dependency of the partial flow back to the tank of the delivery rate of the pump as a function of its speed.

In Fig. 1 ist mit 1 eine Konstantpumpe bezeichnet, die von ei­ ner Asynchronmaschine 2 angetrieben wird. Die Drehzahländerung der Asynchronmaschine erfolgt über einen Frequenzumrichter 3, der eingangsseitig mit einem Drehstromnetz 4 verbunden ist. Der Frequenzumrichter 3 wird von einer elektronischen Steuerung 5 angesteuert, die die Drehzahl der Asynchronmaschine und damit die Drehzahl der Konstantpumpe 1 bestimmt. Die Druckleitung 6 der Konstantpumpe führt über ein 2-Wegeventil 7 mit den Endstel­ lungen a und b zum als Plungerzylinder ausgebildeten Hubzylinder 8. Zwischen Konstantpumpe 1 und 2-Wegeventil 7 führt von der Druckleitung 6 eine Bypass-Leitung 9 über eine Verstelldrossel 10 mit Verstelleinrichtung 11 zurück zum Tank T. Die Verstel­ leinrichtung 11 der Verstelldrossel 10 wird von der gleichen Steuerung 5 angesteuert wie der Frequenzumrichter 3 zur Festle­ gung der Drehzahl n der die Konstantpumpe 1 antreibenden Asyn­ chronmaschine 2. Bei Stillstand der Konstantpumpe 1, also bei Drehzahl n = null, weist entsprechend Fig. 2 die Verstelldros­ sel 10 ihren größten Durchflußquerschnitt A auf. Bei Inbetrieb­ nahme der Konstantpumpe strömt deshalb zunächst der gesamte noch geringe Förderstrom der Konstantpumpe über die Bypass-Leitung 9 mit voll geöffneter Verstelldrossel 10 drucklos zurück zum Tank T. Das in der Druckleitung 6 angeordnete 2-Wegeventil 7 befindet sich beim Stillstand der Pumpe in der einen Endstellung a, in der sich die vom Hubzylinder 8 getragene Last L über die im Ar­ beitsraum 8a des Hubzylinders sowie im Druckleitungsabschnitt 6a befindliche Arbeitsflüssigkeit auf den Rückschlagventilkörper 7a abstützt. Mit zunehmender Drehzahl der Konstantpumpe 1 und damit größer werdenden Fördermenge wird der Durchflußquerschnitt A der Verstelldrossel 10 verkleinert, so daß sich ein überproportiona­ ler Anstieg des Pumpendruckes einstellt. Sobald dieser Pumpen­ druck den im Hubzylinder 8 wirkenden Lastdruck übersteigt, strömt Arbeitsflüssigkeit über den sich öffnenden Rückschlagkör­ per 7a des 2-Wegeventils 7 zum Arbeitsraum 8a des Hubzylinders 8 und verschiebt den die Last tragenden Plunger 12 nach außen bzw. nach oben, wobei eine Teilmenge der Fördermenge der Konstantpum­ pe entsprechend dem aktuellen Durchflußquerschnitt der Ver­ stelldrossel 10 und dem Pumpendruck über die Bypass-Leitung 9 zurück zum Tank strömt. Mit weiter ansteigender Drehzahl der Pumpe und damit steigender Hubgeschwindigkeit des Plungers 12 des Hubzylinders 8 wird der Durchflußquerschnitt der Ver­ stelldrossel 10 weiter verkleinert, bis er schließlich ab einer durch die Steuerung 5 festgelegten Drehzahl n der Konstantpumpe ganz geschlossen wird (Fig. 2), so daß ab diesem Zeitpunkt die gesamte Fördermenge der Konstantpumpe zur Bewegungsumsetzung durch den Plunger 12 des Hubzylinders 8 zur Verfügung steht.In Fig. 1, 1 denotes a constant pump which is driven by egg ner asynchronous machine 2 . The speed change of the asynchronous machine takes place via a frequency converter 3 , which is connected on the input side to a three-phase network 4 . The frequency converter 3 is controlled by an electronic control 5 , which determines the speed of the asynchronous machine and thus the speed of the constant pump 1 . The pressure line 6 of the constant pump leads via a 2-way valve 7 with the end positions a and b to the lifting cylinder designed as a plunger cylinder 8 . Between constant pump 1 and 2-way valve 7 leads from the pressure line 6 a bypass line 9 via an adjusting throttle 10 with adjusting device 11 back to the tank T. The adjusting device 11 of the adjusting throttle 10 is controlled by the same controller 5 as the frequency converter 3 to the Festle supply the rotational speed of the fixed displacement pump 1 driving Asyn n chronmaschine. 2 When the constant pump 1 is at a standstill, that is to say at a speed n = zero, the selector throttle sel 10 has its largest flow cross-section A according to FIG . When putting the constant pump into operation, the entire still low flow rate of the constant pump flows via the bypass line 9 with the fully open adjusting throttle 10 back to the tank T. The 2-way valve 7 arranged in the pressure line 6 is in the position when the pump is at a standstill an end position a, in which the load L borne by the lifting cylinder 8 is supported on the check valve body 7 a by the working fluid located in the working space 8 a of the lifting cylinder and in the pressure line section 6 a. With increasing speed of the constant pump 1 and thus increasing flow rate, the flow cross section A of the adjusting throttle 10 is reduced, so that a disproportionate increase in the pump pressure occurs. As soon as this pump pressure exceeds the load pressure acting in the lifting cylinder 8 , working fluid flows over the opening Rückschlagkör by 7 a of the 2-way valve 7 to the working chamber 8 a of the lifting cylinder 8 and moves the load-bearing plunger 12 to the outside or up, whereby a subset of the delivery rate of the constant pump pe flows according to the current flow cross section of the adjusting throttle 10 and the pump pressure via the bypass line 9 back to the tank. With further increasing speed of the pump and thus increasing stroke speed of the plunger 12 of the lifting cylinder 8 , the flow cross section of the adjusting throttle 10 is further reduced until it is finally closed completely from a speed n of the constant pump determined by the controller 5 ( FIG. 2), so that from this point in time the entire delivery rate of the constant pump is available for motion conversion by the plunger 12 of the lifting cylinder 8 .

Der maximale Durchflußquerschnitt der Verstelldrossel 10 wird so groß gewählt, daß bei langsamer Hubgeschwindigkeit des Plungers über die Bypass-Leitung eine so große Teilmenge des Förderstro­ mes der Pumpe strömen kann, daß letztere für den zum Anheben der Last erforderlichen Druck mit einer Drehzahl betrieben werden muß, die eine ausreichende Schmierung der betreffenden Pumpen­ teile gewährleistet und die Frequenz der Druckpulsation der Pum­ pe die Hubbewegung des Plungers 12 nicht mehr nachteilig beein­ trächtigt.The maximum flow cross section of the adjusting throttle 10 is chosen so large that at a slow stroke speed of the plunger via the bypass line, such a large part of the delivery flow meter of the pump can flow that the latter must be operated at a speed for the pressure required to raise the load which ensures sufficient lubrication of the pump in question and the frequency of the pressure pulsation of the pump pe no longer adversely affects the stroke movement of the plunger 12 .

Die vorbeschriebene Hubeinrichtung wird vorteilhafterweise als Antrieb für einen Aufzug eingesetzt.The lifting device described above is advantageously used as Drive used for an elevator.

Claims (7)

1. Hydraulische Hubeinrichtung bestehend aus einem Hubzy­ linder und einer Konstantpumpe in Kolbenbauart als Druckmittel­ quelle sowie einem drehzahlregelbaren Elektromotor zum Antrieb der Konstantpumpe, dadurch gekennzeichnet, daß ein Teil der För­ dermenge der Konstantpumpe (1) zum Tank (T) zurückführbar ist.1. Hydraulic lifting device consisting of a Hubzy cylinder and a constant pump in piston design as a pressure medium source and a speed-adjustable electric motor for driving the constant pump, characterized in that part of the quantity of the constant pump ( 1 ) is recyclable to the tank (T). 2. Hydraulische Hubeinrichtung nach Anspruch 1, dadurch ge­ kennzeichnet, daß der zum Tank zurückgeführte Teil der Förder­ menge über eine Verstelldrossel (10) geführt wird.2. Hydraulic lifting device according to claim 1, characterized in that the part of the conveyed quantity returned to the tank is guided via an adjusting throttle ( 10 ). 3. Hydraulische Hubeinrichtung nach Anspruch 2, dadurch ge­ kennzeichnet, daß mit zunehmender Drehzahl (n) der Konstantpumpe (1) der Durchflußquerschnitt der Verstelldrossel (10) verklei­ nert wird.3. Hydraulic lifting device according to claim 2, characterized in that with increasing speed (n) of the constant pump ( 1 ) the flow cross section of the variable throttle ( 10 ) is reduced. 4. Hydraulische Hubeinrichtung nach den Ansprüchen 2 und 3, dadurch gekennzeichnet, daß der Durchflußquerschnitt der Ver­ stelldrossel (10) bei der Drehzahl null der Konstantpumpe seinen Größtwert aufweist und ab einer vorbestimmten Drehzahl der Kon­ stantpumpe die Verstelldrossel gesperrt ist.4. Hydraulic lifting device according to claims 2 and 3, characterized in that the flow cross-section of the adjusting throttle Ver ( 10 ) has its maximum value at zero speed of the constant pump and from a predetermined speed of the Kon constant pump is blocked, the variable throttle. 5. Hydraulische Hubeinrichtung nach einem der vorhergehen­ den Ansprüche, dadurch gekennzeichnet, daß die Verstellung der Verstelldrossel (10) durch elektronische Steuermittel (5) er­ folgt.5. Hydraulic lifting device according to one of the preceding claims, characterized in that the adjustment of the adjusting throttle ( 10 ) by electronic control means ( 5 ) it follows. 6. Hydraulische Hubeinrichtung nach einem der vorhergehen­ den Ansprüche, dadurch gekennzeichnet, daß die Verstellung der Verstelldrossel (10) durch mechanische Steuermittel nach dem Fliehkraft-Prinzip erfolgt.6. Hydraulic lifting device according to one of the preceding claims, characterized in that the adjustment of the adjusting throttle ( 10 ) is carried out by mechanical control means according to the centrifugal force principle. 7. Hydraulische Hubeinrichtung nach Anspruch 5 oder 6, da­ durch gekennzeichnet, daß Verstelldrossel (10) und Steuermittel in oder an der Konstantpumpe angeordnet sind.7. Hydraulic lifting device according to claim 5 or 6, characterized in that the adjusting throttle ( 10 ) and control means are arranged in or on the constant pump.
DE19631804A 1996-07-10 1996-08-07 Hydraulic lifting device Expired - Lifetime DE19631804B4 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE19631804A DE19631804B4 (en) 1996-07-10 1996-08-07 Hydraulic lifting device

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19627710 1996-07-10
DE19627710.8 1996-07-10
DE19631804A DE19631804B4 (en) 1996-07-10 1996-08-07 Hydraulic lifting device

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Publication Number Publication Date
DE19631804A1 true DE19631804A1 (en) 1998-01-15
DE19631804B4 DE19631804B4 (en) 2010-02-25

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0990802A2 (en) 1998-09-30 2000-04-05 Robert Bosch Gmbh Electrohydraulic speed control device for an hydraulic lifting cylinder
CN1079073C (en) * 1998-06-08 2002-02-13 液压驱动工业株式会社 Method of controlling energy-efficient hydraulic lifting system
US6769894B2 (en) 2000-10-13 2004-08-03 Engel Maschinenbau Gesellschaft M.B.H. Apparatus for the injection molding of plastic material
WO2005057020A1 (en) * 2003-12-15 2005-06-23 Plugging Specialists International Asa Control system for hydraulic cylinder, plug with a hydraulic cylinder and methods for setting and releasing a plug
CN102042273A (en) * 2010-08-13 2011-05-04 长沙中联重工科技发展股份有限公司 Hydraulic control loop and method
EP3127855A1 (en) * 2015-08-06 2017-02-08 Sherpa Autodiagnostik GmbH Drive for an electrohydraulically operated lifting device, in particular lifting platform

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GB2625568A (en) * 2022-12-20 2024-06-26 Hyva Holding Bv A hydraulic cylinder assembly

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EP0990802A2 (en) 1998-09-30 2000-04-05 Robert Bosch Gmbh Electrohydraulic speed control device for an hydraulic lifting cylinder
EP0990802A3 (en) * 1998-09-30 2001-07-25 Robert Bosch Gmbh Electrohydraulic speed control device for an hydraulic lifting cylinder
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WO2012019498A1 (en) * 2010-08-13 2012-02-16 长沙中联重工科技发展股份有限公司 Hydraulic control circuit and method
EP3127855A1 (en) * 2015-08-06 2017-02-08 Sherpa Autodiagnostik GmbH Drive for an electrohydraulically operated lifting device, in particular lifting platform
DE102015112974A1 (en) * 2015-08-06 2017-02-09 Sherpa Autodiagnostik Gmbh Drive for an electrohydraulic lifting device, in particular lifting platform

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