EP2655895A1 - Hydraulic drive - Google Patents

Hydraulic drive

Info

Publication number
EP2655895A1
EP2655895A1 EP11784424.1A EP11784424A EP2655895A1 EP 2655895 A1 EP2655895 A1 EP 2655895A1 EP 11784424 A EP11784424 A EP 11784424A EP 2655895 A1 EP2655895 A1 EP 2655895A1
Authority
EP
European Patent Office
Prior art keywords
pump
hydraulic
pressure
torque
variable
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
EP11784424.1A
Other languages
German (de)
French (fr)
Other versions
EP2655895B1 (en
Inventor
Patric BUECKER
Stefan NIEDERNHOEFER
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2655895A1 publication Critical patent/EP2655895A1/en
Application granted granted Critical
Publication of EP2655895B1 publication Critical patent/EP2655895B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • F04B17/00—Pumps characterised by combination with, or adaptation to, specific driving engines or motors
    • F04B17/03—Pumps characterised by combination with, or adaptation to, specific driving engines or motors driven by electric motors
    • 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
    • F04B49/06—Control using electricity
    • F04B49/065—Control using electricity and making use of computers
    • 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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B2203/00—Motor parameters
    • F04B2203/02—Motor parameters of rotating electric motors
    • F04B2203/0207—Torque
    • 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
    • F04B2205/06—Pressure in a (hydraulic) circuit
    • 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
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/26—Power control functions
    • 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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply pressure
    • 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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/633—Electronic controllers using input signals representing a state of the prime mover, e.g. 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6333—Electronic controllers using input signals representing a state of the pressure source, e.g. swash plate angle
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • 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
    • F15B2211/6655—Power control, e.g. combined pressure and flow rate control

Definitions

  • the present invention relates to a hydraulic drive for a hydraulic consumer according to the preamble of patent claim 1.
  • EP 0 805 922 B1 discloses a hydraulic pump control system of an aircraft using a variable displacement hydraulic pump driven by a variable speed electric motor.
  • the speed of the motor is hereby controlled so that its reduction rate at a system request reduction is smaller than its increase rate at a system request magnification. This means that, for example, with decreasing demand pressure, the first
  • Stroke volume of the pump is reduced, whereas at increasing demand pressure initially increases the engine speed.
  • EP 464 286 B1 Another prior art is EP 464 286 B1, from which an electro-hydraulic drive unit is also known.
  • This drive unit uses a variable speed operable electric motor for driving a variable displacement pump.
  • the variable displacement pump is adjusted by means of a spring to a position with maximum displacement, from which it is adjusted in the direction of minimum displacement when the pressure in the hydraulic system rises above a certain pressure value.
  • DE 10 2007 007 005 A1 discloses an electro-hydraulic control arrangement with a displacement-variable pump which is driven by a variable-speed electric motor.
  • a two-position regulator is provided, which switches the pump to a maximum or minimum delivery position, depending on an overflow or underflow condition with respect to a pressure threshold.
  • the invention accordingly relates to a hydraulic drive for one or more consumers or to a hydraulic system with a displacement-variable pump, which is mechanically coupled to a variable-speed drive motor, and a controller for adjusting the stroke volume of the pump.
  • the pump is torque-controlled. This means that to drive the pump a certain torque should not be exceeded.
  • the torque which results from the product of system pressure and stroke volume, which is referred to as the amount of pressure fluid delivered by the pump per revolution, is below the specified torque even at maximum displacement, the torque control does not intervene.
  • Acceleration and load at the stop by a pressure valve can be specified so high that the product of pressure and stroke volume reaches the predetermined value, the pump is adjusted in the direction of smaller displacement.
  • the product of pressure and stroke volume remains at least approximately constant.
  • a drive motor with a relatively small maximum torque can be used, making the drive more cost effective and also its operation by reduced power consumption of the engine is more economical.
  • torque detection device is here to be used to designate any device which is capable of drawing conclusions about the current torque load of the drive motor, for example a torque sensor which is placed on the drive motor or its output shaft Current measuring device, which measures the actual current consumption of the motor and determines its output torque.It is also possible to detect the current pressure in the hydraulic system connected downstream of the pump and to control or regulate the stroke volume so that the specified maximum torque is not exceeded.
  • Torque detection / or determination device for a variable displacement known per se, in which a valve piston of a control valve in the one adjustment of a spring force, which sets the maximum torque, and in the other adjustment direction is acted upon by a force that resulting from the stroke volume dependent point of attack of a pump pressure applied to the piston on a lever.
  • the drive motor is variable in speed.
  • the stroke volume of the pump is reduced to limit the required torque on the engine, this would result in a hydraulically induced movement of one or more consumers (eg, a lift cylinder) slowing down.
  • the speed of the drive motor can be increased with reduced displacement of the pump, whereby the volume flow generated by the swung back pump speed increases again without the output torque increases.
  • the hydraulic load is at a stop when the pressure rises, only one pressure is to be maintained, so that the speed of the drive motor does not increase, on the contrary, it is more likely to decrease.
  • the power consumption of the engine can be kept below a substantially (quasi) constant value, so that the engine with respect to its maximum possible
  • Power output can be designed smaller.
  • Fig. 1 shows in juxtaposition
  • Fig. 2 shows a hydraulic control / control for a
  • variable displacement pump according to the invention.
  • Hydraulic drive shown using two independently driven constant displacement pumps. Each pump is therefore driven by its own, possibly variable-speed motor. This structure is comparatively complicated and expensive. In addition, there is a large amount of space, making this solution rather uneconomical.
  • An improvement provides the well-known hydraulic drive according to the middle representation in the figure. This drive also uses two fixed displacement pumps, but they are driven together by a single motor.
  • One of the constant-displacement pumps can be connected via a valve, a 2/2-way valve with an open position and a blocking position can optionally be switched directly to a tank, whereby this pump is taken from the downstream hydraulic system. In this way, the engine can be relieved.
  • the pump 2 may be designed as a swash plate pump whose swash plate inclination is continuously or stepwise variable.
  • This pump 2 is connected on the output side to a hydraulic system 4, for example consisting of an actuating valve 6, via which a consumer 8, in this case a piston-cylinder unit can be actuated.
  • the only displacement-variable pump 2 is operated by a single, preferably variable-speed drive motor 10, for example an electric motor, which is mechanically coupled to the pump 2 via a drive shaft.
  • a single, preferably variable-speed drive motor 10 for example an electric motor, which is mechanically coupled to the pump 2 via a drive shaft.
  • a control unit 11 is provided for the drive motor 10, to which at least one torque sensor and a system pressure sensor and a speed sensor and a sensor for detecting the currently set stroke volume (swash plate tilt) of the pump 2 are connected (all sensors are not shown).
  • the control unit 11 is programmed or programmable so that the hydraulic drive 1 builds up a predeterminable (input) consumer or system pressure and holds it.
  • T Actual output torque of the motor.
  • the drive motor 10 to make variable speed. Therefore, the rotational speed of the engine 10 can be increased as the discharge capacity of the pump 2 is reduced to maintain the output torque constant to maintain the demanded actual consumer pressure.
  • FIG. 2 shows a representation of the pressure medium pump according to the present invention.
  • a housing 12 the hydraulic drive with a cylinder drum 40, a drive shaft 22, a swash plate 43, a Ausschwenkkolben 75 which limits a control chamber 101, a return spring 85 on the Ausschwenkkolben 75 and a Einschwenkkolben 76 which limits a control chamber 102 ,
  • a high-pressure passage 103 and a low-pressure or suction passage 104 run in the housing 12.
  • the actuation chamber 101 is permanently connected to a high-pressure passage 103 via a passage 105.
  • a control valve 80 is constructed on the housing 12.
  • This consists of a torque control valve 06 and a pressure control valve part 107, which in a rest position via a first Input and its control output a control output of the torque control valve 106 switches through to a control line 108 which leads to the control chamber 102 on Einschwenkkolben 76.
  • a second input of the pressure regulating valve 107 is connected to the high pressure passage 103.
  • an input of the torque control valve 106 is connected to the high pressure passage 103, while a second input of this torque control valve 106 is open to tank pressure having interior of the housing 12.
  • a control piston of the pressure control valve 107 is acted upon in the sense of a reduction of the swivel angle of the swash plate 43 from the pressure in the high pressure line 103 and in the opposite direction by an adjustable spring.
  • a two-armed lever 1 15 is mounted, on whose one lever arm guided in the housing of a return element and via the channel 105, the adjusting chamber 101 and the bore 92 in Ausschwenkkolben 75 with the pressure in the high-pressure passage 103 acted piston 116th attacks.
  • the distance of the point of attack changes with the swivel angle of the swashplate 43.
  • the other arm of the lever 115 is located between the one end of a control piston of the torque control valve 106 and an adjustable spring 117 engaging at least approximately opposite the lever arm.
  • the control piston of the torque control valve 106 acted upon by an adjustable spring 118 in the direction of the lever arm.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Computer Hardware Design (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Reciprocating Pumps (AREA)

Abstract

The invention relates to a hydraulic drive for a hydraulic load or for a hydraulic system having a variable-displacement pump which is mechanically coupled to a preferably variable-speed drive motor, and a control for adjusting at least the capacity of the pump and optionally the speed of the drive motor. According to the invention a torque detecting or determining device is provided which detects or calculates a current output torque of the drive motor, wherein in response thereto the capacity of the pump is set to a value at which the current output torque is at or below a set maximum value.

Description

Hydraulischer Antrieb  Hydraulic drive
Beschreibung description
Die vorliegende Erfindung betrifft einen hydraulischen Antrieb für einen hydraulischen Verbraucher gemäß dem Oberbegriff des Patentanspruchs 1. The present invention relates to a hydraulic drive for a hydraulic consumer according to the preamble of patent claim 1.
Aus dem Stand der Technik gemäß der EP 1 387 090 A2 ist ein hydraulischer Antrieb dieser Gattung bekannt. Dieser sieht die Anordnung eines drehzahlvariablen Elektromotors vor, der in diesem Fall zwei Konstantpumpen antreibt. Zumindest eine der Pumpen ist in Abhängigkeit des aktuellen Verbraucherdrucks zu-/abschaltbar, indem diese Pumpe vorzugsweise mit dem größeren Hubvolumen wahlweise auf Umlauf geschaltet wird. Auf diese Weise kann der motorische Antrieb mit vergleichsweise kleinem Drehmoment ausgelegt sein. From the prior art according to EP 1 387 090 A2, a hydraulic drive of this type is known. This provides for the arrangement of a variable-speed electric motor, which in this case drives two constant-displacement pumps. At least one of the pumps can be switched on / off as a function of the current consumer pressure, by this pump preferably being switched to circulation with the larger displacement volume. In this way, the motor drive can be designed with a comparatively small torque.
Die EP 0 805 922 B1 offenbart ein Hydraulikpumpen-Steuersystem eines Flugzeugs, das eine verdrängungsvariable Hydropumpe verwendet, die von einem drehzahlvariablen Elektromotor angetrieben wird. Die Drehzahl des Motors wird hierbei so geregelt, dass dessen Verkleinerungsrate bei einer Systemanforderungs-Verringerung kleiner ist als dessen Erhöhungsrate bei einer Systemanforderungs-Vergrößerung. Das bedeutet, dass beispielsweise bei sich verringerndem Bedarfsdruck zuerst das EP 0 805 922 B1 discloses a hydraulic pump control system of an aircraft using a variable displacement hydraulic pump driven by a variable speed electric motor. The speed of the motor is hereby controlled so that its reduction rate at a system request reduction is smaller than its increase rate at a system request magnification. This means that, for example, with decreasing demand pressure, the first
Hubvolumen der Pumpe reduziert wird, wohingegen bei sich erhöhendem Bedarfsdruck zunächst die Motordrehzahl steigt. Stroke volume of the pump is reduced, whereas at increasing demand pressure initially increases the engine speed.
Als weiterer Stand der Technik sei die EP 464 286 B1 genannt, aus der ebenfalls eine elektro-hydraulische Antriebseinheit bekannt ist. Diese Antriebseinheit verwendet einen drehzahlvariabel betreibbaren Elektromotor zum Antreiben einer Verstellpumpe. Die Verstellpumpe ist dabei mittels einer Feder auf eine Position mit maximalem Hubvolumen eingestellt, aus der sie in Richtung minimalem Hubvolumen verstellt wird, wenn der Druck im Hydrauliksystem über einen bestimmten Druckwert ansteigt. Die DE 10 2007 007 005 A1 offenbart schließlich eine elektro-hydraulische Steueranordnung mit einer verdrängungsvariablen Pumpe, die von einem drehzahlvariablen Elektromotor angetrieben wird. Zur Steuerung der Pumpe ist ein Zweipunktregler vorgesehen, der die Pumpe auf eine maximale oder minimale Förderposition schaltet und zwar in Abhängigkeit von einem Über- oder Unterschreitungszustand bezüglich eines Druckschwellenwerts. Another prior art is EP 464 286 B1, from which an electro-hydraulic drive unit is also known. This drive unit uses a variable speed operable electric motor for driving a variable displacement pump. The variable displacement pump is adjusted by means of a spring to a position with maximum displacement, from which it is adjusted in the direction of minimum displacement when the pressure in the hydraulic system rises above a certain pressure value. Finally, DE 10 2007 007 005 A1 discloses an electro-hydraulic control arrangement with a displacement-variable pump which is driven by a variable-speed electric motor. To control the pump, a two-position regulator is provided, which switches the pump to a maximum or minimum delivery position, depending on an overflow or underflow condition with respect to a pressure threshold.
Ausgehend von dem vorstehend genannten Stand der Technik ist es eine Aufgabe der vorliegenden Erfindung, einen hydraulischen Antrieb für ein Hydrauliksystem bereitzustellen, zumindest bestehend aus einer verdrängungsvariablen (variables Hubvolumen) Druckmittelquelle (Hydropumpe) und einem drehzahlvariablen Antriebsmotor, wobei der Antrieb gegenüber dem Stand der Technik verbesserte Eigenschaften aufweist. Ein Ziel ist es, den hydraulischen Antrieb kostengünstiger zu machen. Ein weiteres Ziel ist es, den regelungstechnischen Aufwand zu verringern. Schließlich ist es ein Ziel der vorliegenden Erfindung, nach dem Konstruktionsprinzip des„downsizing" insbesondere den Antriebsmotor leistungsmäßig zu verkleinern, ohne dass die Based on the aforementioned prior art, it is an object of the present invention to provide a hydraulic drive for a hydraulic system, at least consisting of a variable displacement (variable displacement) pressure medium source (hydraulic pump) and a variable speed drive motor, the drive over the prior art has improved properties. One goal is to make the hydraulic drive more cost effective. Another goal is to reduce the control engineering effort. Finally, it is an object of the present invention, according to the design principle of "downsizing" in particular to reduce the power of the drive motor, without the
Funktionssicherheit des nachgeschalteten Hydrauliksystems gefährdet wird. Functional safety of the downstream hydraulic system is compromised.
Die gestellte Aufgabe wird durch einen hydraulischen Antrieb mit den Merkmalen des Patentanspruchs 1 gelöst. Vorteilhafte Ausgestaltungen der Erfindung sind Gegenstand der Unteransprüche. The stated object is achieved by a hydraulic drive having the features of patent claim 1. Advantageous embodiments of the invention are the subject of the dependent claims.
Die Erfindung betrifft demzufolge einen hydraulischen Antrieb für einen/mehrere Verbraucher oder für ein Hydrauliksystem mit einer verdrängungsvariablen Pumpe, die mechanisch mit einem drehzahlvariablen Antriebsmotor gekoppelt ist, und einer Steuerung zur Verstellung des Hubvolumens der Pumpe. Erfindungsgemäß ist die Pumpe drehmomentgeregelt. Das heißt, dass zum Antrieb der Pumpe ein bestimmtes Drehmoment nicht überschritten werden soll. Solange das Drehmoment, das sich aus dem Produkt von Systemdruck und Hubvolumen, als das man die von der Pumpe pro Umdrehung geförderte Druckmittelmenge bezeichnet, ergibt, auch bei maximalen Hubvolumen unterhalb des bestimmten Drehmoments liegt, greift die Drehmomentregelung nicht ein. Wird der Druck, der durch die Last bestimmt ist oder bei The invention accordingly relates to a hydraulic drive for one or more consumers or to a hydraulic system with a displacement-variable pump, which is mechanically coupled to a variable-speed drive motor, and a controller for adjusting the stroke volume of the pump. According to the invention, the pump is torque-controlled. This means that to drive the pump a certain torque should not be exceeded. As long as the torque, which results from the product of system pressure and stroke volume, which is referred to as the amount of pressure fluid delivered by the pump per revolution, is below the specified torque even at maximum displacement, the torque control does not intervene. Will the pressure that is determined by the load or at
Beschleunigungsvorgängen und bei Last am Anschlag durch ein Druckventil vorgegeben werden kann, so hoch, dass das Produkt aus Druck und Hubvolumen den vorgegebenen Wert erreicht, so wird die Pumpe in Richtung kleineres Hubvolumen verstellt. Das Produkt aus Druck und Hubvolumen bleibt wenigstens annähernd konstant. Acceleration and load at the stop by a pressure valve can be specified so high that the product of pressure and stroke volume reaches the predetermined value, the pump is adjusted in the direction of smaller displacement. The product of pressure and stroke volume remains at least approximately constant.
In diesem Fall kann ein Antriebsmotor mit einem relativ kleinen maximalen Drehmoment verwendet werden, wodurch der Antrieb insgesamt kostengünstiger und auch dessen Betrieb durch verringerte Leistungsaufnahme des Motors wirtschaftlicher wird. In this case, a drive motor with a relatively small maximum torque can be used, making the drive more cost effective and also its operation by reduced power consumption of the engine is more economical.
Unter dem Begriff„Drehmomenterfassungs-/ oder Bestimmungseinrichtung" ist hierbei jede Einrichtung zu versehen, die geeignet ist, Rückschlüssen auf die aktuelle Drehmomentbelastung des Antriebsmotors zu ziehen. Diese Einrichtung kann beispielsweise ein Drehmomentsensor sein, der am Antriebsmotor bzw. dessen Abtriebswelle platziert ist oder ein Strommessgerät, das die aktuelle Stromaufnahme des Motors misst und hieraus sein abgegebenes Drehmoment bestimmt. Auch besteht die Möglichkeit, der aktuellen Druck im der Pumpe nachgeschalteten Hydrauliksystem zu erfassen und das Hubvolumen gesteuert oder geregelt so zu verstellen, dass das vorgegebene maximale Drehmoment nicht überschritten wird. The term "torque detection device" is here to be used to designate any device which is capable of drawing conclusions about the current torque load of the drive motor, for example a torque sensor which is placed on the drive motor or its output shaft Current measuring device, which measures the actual current consumption of the motor and determines its output torque.It is also possible to detect the current pressure in the hydraulic system connected downstream of the pump and to control or regulate the stroke volume so that the specified maximum torque is not exceeded.
Besonders bevorzugt wird als„Drehmomenterfassungs-/ oder Bestimmungseinrichtung" ein für Verstellpumpe an sich bekannter Drehmomentregler, bei dem ein Ventilkolben eines Regelventils in die eine Verstellrichtung von einer Federkraft, die das Maximalmoment vorgibt, und in die andere Verstellrichtung von einer Kraft beaufschlagt wird, die sich aus dem vom Hubvolumen abhängigen Angriffspunkt eines vom Pumpendruck beaufschlagten Kolbens an einem Hebel ergibt. Particularly preferred as "Torque detection / or determination device" for a variable displacement known per se, in which a valve piston of a control valve in the one adjustment of a spring force, which sets the maximum torque, and in the other adjustment direction is acted upon by a force that resulting from the stroke volume dependent point of attack of a pump pressure applied to the piston on a lever.
Der Antriebsmotor ist drehzahlvariabel. Wird demnach das Hubvolumen der Pumpe reduziert, um das erforderliche Drehmoment am Motor zu begrenzen, würde dies dazu führen, dass sich eine hydraulisch bewirkte Bewegung eines oder mehrer Verbraucher (beispielsweise ein Hubzylinder) verlangsamt. Will man die Bewegung beibehalten, so kann die Drehzahl des Antriebsmotors bei verringertem Hubvolumen der Pumpe erhöht werden, wodurch der von der zurückgeschwenkten Pumpe erzeugte Volumenstrom drehzahlabhängig wieder steigt, ohne dass das Abgabedrehmoment zunimmt. Steht der hydraulische Verbraucher jedoch an einem Anschlag, wenn der Druck ansteigt, ist nur ein Druck zu halten, so dass die Drehzahl des Antriebsmotors nicht zu erhöhen, im Gegenteil, eher zu verringern ist. The drive motor is variable in speed. Thus, if the stroke volume of the pump is reduced to limit the required torque on the engine, this would result in a hydraulically induced movement of one or more consumers (eg, a lift cylinder) slowing down. If you want to maintain the movement, the speed of the drive motor can be increased with reduced displacement of the pump, whereby the volume flow generated by the swung back pump speed increases again without the output torque increases. However, if the hydraulic load is at a stop when the pressure rises, only one pressure is to be maintained, so that the speed of the drive motor does not increase, on the contrary, it is more likely to decrease.
Durch die direkt/indirekt drehmomentabhängige Regelung der Druckmittelquelle kann die Leistungsaufnahme des Motors unterhalb eines im Wesentlichen (quasi) konstanten Werts gehalten werden, sodass der Motor hinsichtlich seiner maximal möglichen Due to the direct / indirect torque-dependent control of the pressure medium source, the power consumption of the engine can be kept below a substantially (quasi) constant value, so that the engine with respect to its maximum possible
Leistungsabgabe kleiner konzipiert werden kann. Power output can be designed smaller.
Die Erfindung wird nachstehend anhand eines bevorzugten Ausführungsbeispiels unter Bezugnahme auf die begleitenden Figuren näher erläutert. The invention will be explained below with reference to a preferred embodiment with reference to the accompanying figures.
Fig. 1 zeigt dabei in Gegenüberstellung Fig. 1 shows in juxtaposition
- einen hydraulischen Antrieb mit zwei individuell angetrieben Pumpen kleinen Hubvolumens gemäß dem Stand der Technik,  a hydraulic drive with two individually driven pumps small displacement according to the prior art,
- einen hydraulisch Antrieb mit einer permanenten und einer zuschaltbaren  - a hydraulic drive with a permanent and a switchable
Konstantpumpe gemäß dem Stand der Technik und  Constant pump according to the prior art and
- einen hydraulischen Antrieb mit einer drehmomentgesteuerten, verdrängungsvariablen Pumpe und einem drehzahlvariablen Antriebsmotor gemäß einem bevorzugten Ausführungsbeispiel der Erfindung und  - A hydraulic drive with a torque-controlled, variable displacement pump and a variable speed drive motor according to a preferred embodiment of the invention and
Fig. 2 zeigt eine hydraulische Regelung/Steuerung für eine Fig. 2 shows a hydraulic control / control for a
- Druckmittelquelle insbesondere eine  - Pressure medium source in particular a
- verdrängungsvariable Pumpe gemäß der Erfindung.  variable displacement pump according to the invention.
Gemäß der anliegenden Fig.1 ist in der linken Darstellung ein bereits bekannter According to the appended FIG. 1, an already known one is shown in the left-hand illustration
Hydraulikantrieb gezeigt, der zwei unabhängig angetriebene Konstantpumpen verwendet. Jede Pumpe wird folglich von einem eigenen, ggf. drehzahlvariablen Motor angetrieben. Dieser Aufbau ist vergleichsweise aufwändig und teuer. Außerdem besteht ein großer Platzbedarf, wodurch diese Lösung eher unwirtschaftlich ist. Eine Verbesserung erbringt der ebenfalls bekannte Hydraulikantrieb gemäß der in der Figur mittleren Darstellung. Dieser Antrieb verwendet ebenfalls zwei Konstantpumpen, die jedoch von einem einzigen Motor gemeinsam angetrieben werden. Eine der Konstantpumpen lässt sich über ein Ventil, vorliegen ein 2/2-Schaltventil mit einer Offen- und einer Sperrposition wahlweise direkt auf einen Tank schalten, wodurch diese Pumpe aus dem nachgeschalteten Hydrauliksystem genommen wird. Auf diese Weise kann der Motor entlastet werden. Hydraulic drive shown using two independently driven constant displacement pumps. Each pump is therefore driven by its own, possibly variable-speed motor. This structure is comparatively complicated and expensive. In addition, there is a large amount of space, making this solution rather uneconomical. An improvement provides the well-known hydraulic drive according to the middle representation in the figure. This drive also uses two fixed displacement pumps, but they are driven together by a single motor. One of the constant-displacement pumps can be connected via a valve, a 2/2-way valve with an open position and a blocking position can optionally be switched directly to a tank, whereby this pump is taken from the downstream hydraulic system. In this way, the engine can be relieved.
Die gemäß der anliegenden Figur rechte Darstellung zeigt hingegen einen hydraulischen Antrieb 1 gemäß der vorliegenden Erfindung. In contrast, the right-hand illustration according to the appended FIGURE shows a hydraulic drive 1 according to the present invention.
Demzufolge ist nur eine einzige Pumpe 2 vorgesehen, die verdrängungsvariabel ausgebildet ist. Beispielsweise kann die Pumpe 2 als Schrägscheibenpumpe ausgeführt sein, deren Schrägscheibenneigung kontinuierlich oder schrittweise veränderbar ist. Diese Pumpe 2 ist ausgangsseitig an ein Hydrauliksystem 4 angeschlossen, beispielsweise bestehend aus einem Betätigungsventil 6, über welches ein Verbraucher 8, vorliegend eine Kolben-Zylinder-Einheit betätigbar ist. As a result, only a single pump 2 is provided, which is designed to be variable in displacement. For example, the pump 2 may be designed as a swash plate pump whose swash plate inclination is continuously or stepwise variable. This pump 2 is connected on the output side to a hydraulic system 4, for example consisting of an actuating valve 6, via which a consumer 8, in this case a piston-cylinder unit can be actuated.
Die einzige verdrängungsvariable Pumpe 2 wird von einem einzigen, vorzugsweise drehzahlvariablen Antriebsmotor 10, beispielsweise ein Elektromotor, betrieben, der über eine Antriebswelle mit der Pumpe 2 mechanisch gekoppelt ist. The only displacement-variable pump 2 is operated by a single, preferably variable-speed drive motor 10, for example an electric motor, which is mechanically coupled to the pump 2 via a drive shaft.
Schließlich ist eine Steuereinheit 11 für den Antriebsmotor 10 vorgesehen, an die vorliegend zumindest ein Drehmomentsensor und ein Systemdrucksensor sowie ein Drehzahlsensor und ein Sensor zur Erfassung des aktuell eingestellten Hubvolumens (Schrägscheibenneigung) der Pumpe 2 angeschlossen sind (sämtliche Sensoren sind nicht dargestellt). Die Steuereinheit 11 ist dabei so programmiert oder programmierbar, dass der Hydraulikantrieb 1 einen vorbestimmbaren (eingebbaren) Verbraucher- oder Systemdruck aufbaut und diesen hält. Finally, a control unit 11 is provided for the drive motor 10, to which at least one torque sensor and a system pressure sensor and a speed sensor and a sensor for detecting the currently set stroke volume (swash plate tilt) of the pump 2 are connected (all sensors are not shown). The control unit 11 is programmed or programmable so that the hydraulic drive 1 builds up a predeterminable (input) consumer or system pressure and holds it.
Erfindungsgemäß ist ein Antriebsmotor 10 mit vergleichsweise geringer Leistung verbaut, der nur ein geringes maximales Abgabedrehmoment ermöglicht. Daher wird bei Erreichen dieses maximalen Abgabedrehmoments oder bereits darunter, beispielsweise im Fall eines Druckanstiegs im Hydrauliksystem die verdrängungsvariable Pumpe 2 zurückgefahren, d.h. deren Förderkapazität verringert, wodurch sich das aktuelle Abgabemoment des Antriebsmotors 10 reduziert. Auf diese Weise kann die Pumpe 2 bzw. deren Hubvolumen so eingestellt werden, dass unabhängig vom Druckzustand im nachgeschalteten Hydrauliksystem das aktuelle Abgabemoment des Motors 0 einen maximalen Drehmomentwert nicht übersteigt oder darunter bleibt. Im günstigen Fall kann das Abgabemoment im Wesentlichen konstant gehalten werden. D.h. es gilt die Gleichung P x V = konst = T, wobei According to the invention a drive motor 10 is installed with comparatively low power, which allows only a small maximum output torque. Therefore, upon reaching this maximum output torque or below, for example in the case of a pressure increase in the hydraulic system, the variable-displacement pump 2 is reduced, ie the delivery capacity is reduced, whereby the current output torque of the drive motor 10 is reduced. In this way, the pump 2 or its displacement can be adjusted so that regardless of the pressure state in the downstream hydraulic system, the current output torque of the motor 0 does not exceed a maximum torque value or remains below. In the favorable case, the output torque can be kept substantially constant. That is, the equation P x V = const = T, where
P: Ist-Druck im Hydrauliksystem P: Actual pressure in the hydraulic system
V: Ist-Hubvolumen der Pumpe V: Actual stroke volume of the pump
T: Ist-Abtriebsmoment des Motors. T: Actual output torque of the motor.
Wird die Förderkapazität der Pumpe 2 in dieser Weise zurückgefahren, würde der am Verbraucher anliegende Hydraulikdruck in der Folge absinken bzw. die hydraulisch aktivierte Bewegung eines Verbrauchers sich verlangsamen. Um dies zu vermeiden, ist es gemäß dem bevorzugten Ausführungsbeispiel der Erfindung optional vorgesehen, den Antriebsmotor 10 drehzahlvariabel zu machen. Daher kann die Drehzahl des Motors 10 bei Verringerung der Förderkapazität der Pumpe 2 zur Konstanthaltung des Abgabedrehmoments angehoben werden, um den geforderten aktuellen Verbraucherdruck bzw. die Verbraucher-Bewegungsgeschwindigkeit aufrecht zu erhalten. If the delivery capacity of the pump 2 is reduced in this way, the hydraulic pressure applied to the consumer would decrease as a result or the hydraulically activated movement of a consumer would slow down. To avoid this, it is optionally provided according to the preferred embodiment of the invention, the drive motor 10 to make variable speed. Therefore, the rotational speed of the engine 10 can be increased as the discharge capacity of the pump 2 is reduced to maintain the output torque constant to maintain the demanded actual consumer pressure.
Bezüglich der Ansteuerung einer solchen Druckmittelquelle bzw. verdrängungsvariablen Pumpe 2 sei auf das Schaltbild nach Fig. 2 verwiesen, das eine Darstellung der Druckmittelpumpe gemäß der vorliegenden Erfindung zeigt. Dort erkennt man in einem Gehäuse 12 den hydraulischen Antrieb mit einer Zylindertrommel 40, einer Triebwelle 22, einer Schrägscheibe 43, einem Ausschwenkkolben 75, der eine Stellkammer 101 begrenzt, einer Rückstellfeder 85 auf dem Ausschwenkkolben 75 und einem Einschwenkkolben 76, der eine Stellkammer 102 begrenzt. Im Gehäuse 12 verlaufen ein Hochdruckkanal 103 und ein Niederdruck- oder Saugkanal 104. Die Stellkammer 101 ist über einen Kanal 105 dauernd mit einem Hochdruckkanal 103 verbunden. Auf das Gehäuse 12 ist ein Regelventil 80 aufgebaut. Dieses besteht aus einem Momentenregelteilventil 06 und einem Druckregelteilventil 107, das in einer Ruhestellung über einen ersten Eingang und seinen Regelausgang einen Regelausgang des Momentenregelteilventils 106 zu einer Steuerleitung 108 durchschaltet, die zu der Stellkammer 102 am Einschwenkkolben 76 führt. Ein zweiter Eingang des Druckregelteilventils 107 ist mit dem Hochdruckkanal 103 verbunden. Ebenso ist ein Eingang des Momentenregelteilventils 106 mit dem Hochdruckkanal 103 verbunden, während ein zweiter Eingang dieses Momentenregelteilventils 106 zum Tankdruck aufweisenden Inneren des Gehäuses 12 offen ist. Ein Regelkolben des Druckregelteilventils 107 wird im Sinne einer Verkleinerung des Schwenkwinkels der Schrägscheibe 43 vom Druck in der Hochdruckleitung 103 und im Gegensinne von einer einstellbaren Feder beaufschlagt. With regard to the control of such a pressure medium source or displacement variable pump 2, reference is made to the diagram of FIG. 2, which shows a representation of the pressure medium pump according to the present invention. There one recognizes in a housing 12 the hydraulic drive with a cylinder drum 40, a drive shaft 22, a swash plate 43, a Ausschwenkkolben 75 which limits a control chamber 101, a return spring 85 on the Ausschwenkkolben 75 and a Einschwenkkolben 76 which limits a control chamber 102 , A high-pressure passage 103 and a low-pressure or suction passage 104 run in the housing 12. The actuation chamber 101 is permanently connected to a high-pressure passage 103 via a passage 105. On the housing 12, a control valve 80 is constructed. This consists of a torque control valve 06 and a pressure control valve part 107, which in a rest position via a first Input and its control output a control output of the torque control valve 106 switches through to a control line 108 which leads to the control chamber 102 on Einschwenkkolben 76. A second input of the pressure regulating valve 107 is connected to the high pressure passage 103. Likewise, an input of the torque control valve 106 is connected to the high pressure passage 103, while a second input of this torque control valve 106 is open to tank pressure having interior of the housing 12. A control piston of the pressure control valve 107 is acted upon in the sense of a reduction of the swivel angle of the swash plate 43 from the pressure in the high pressure line 103 and in the opposite direction by an adjustable spring.
Im Gehäuse 95 des Ventils 80 ist ein zweiarmiger Hebel 1 15 gelagert, an dessen einem Hebelarm ein im Gehäuse eines Rückführelements geführter und über den Kanal 105, die Stellkammer 101 und die Bohrung 92 im Ausschwenkkolben 75 mit dem Druck in dem Hochdruckkanal 103 beaufschlagter Kolben 116 angreift. Die Entfernung des Angriffspunkts ändert sich mit dem Schwenkwinkel der Schrägscheibe 43. Der andere Arm des Hebels 115 befindet sich zwischen dem einen Ende eines Regelkolbens des Momentenregelteilventils 106 und einer wenigstens annähernd gegenüberliegend an dem Hebelarm angreifenden, einstellbaren Feder 117. Weiterhin ist der Regelkolben des Momentenregelteilventils 106 in Richtung auf den Hebelarm von einer einstellbaren Feder 118 beaufschlagt. Die Feder 117 und die Feder 1 18, die schwächer als die Feder 1 17 eingestellt ist, erzeugen an dem Hebel 1 15 ein festes Drehmoment in die eine Richtung. Der Hochdruck im Kanal 03 erzeugt mit Hilfe der Wirkfläche des Kolbens 116 an dem Hebel 1 15 ein Drehmoment, das dem festen Drehmoment entgegengerichtet ist und von der Position des Ausschwenkkolbens 75 oder allgemein vom Schwenkwinkel der Schrägscheibe 43 abhängt. Bei einem gegebenen Druck kann nur bei einem bestimmten Schwenkwinkel dem von den beiden Federn erzeugten Drehmoment das Gleichgewicht gehalten werden. Bei einer Störung des Gleichgewichts durch eine Druckänderung wird der Ventilkolben des Momentenregelteilventils 106 aus seiner Regelposition bewegt, so dass der Stellkammer 102 Druckmittel zufließt oder aus der Stellkammer 102 Druckmittel abfließen kann, bis ein anderen Schwenkwinkel erreicht ist, bei dem wieder Gleichgewicht zwischen den Drehmomenten am Hebel 1 15 herrscht. Erhöht sich demnach der Hydrauliksystemdruck und damit der Druck in der Leitung 103, wird der Ventilkolben des Momentenregelteilventils 106 gemäß der Fig. 2 nach rechts gezogen, wodurch der Systemdruck über die Leitung 108 an den Einschwenkkolben 76 angelegt wird. Dieser reduziert demzufolge die Neigung der Schrägscheibe 43 bis zum Drehmomentausgleich am Hebelarm 115. Das vom Motor abzugebende Antriebsdrehmoment auf die Welle 22 kann somit konstant gehalten werden. In the housing 95 of the valve 80, a two-armed lever 1 15 is mounted, on whose one lever arm guided in the housing of a return element and via the channel 105, the adjusting chamber 101 and the bore 92 in Ausschwenkkolben 75 with the pressure in the high-pressure passage 103 acted piston 116th attacks. The distance of the point of attack changes with the swivel angle of the swashplate 43. The other arm of the lever 115 is located between the one end of a control piston of the torque control valve 106 and an adjustable spring 117 engaging at least approximately opposite the lever arm. Furthermore, the control piston of the torque control valve 106 acted upon by an adjustable spring 118 in the direction of the lever arm. The spring 117 and the spring 1 18, which is set weaker than the spring 1 17, generate on the lever 1 15 a fixed torque in one direction. The high pressure in the channel 03 generated by means of the effective surface of the piston 116 on the lever 1 15, a torque which is opposite to the fixed torque and depends on the position of the Ausschwkolbenkolbens 75 or generally from the pivot angle of the swash plate 43. At a given pressure, only at a certain swing angle can the balance of torque produced by the two springs be maintained. In a disturbance of the equilibrium by a pressure change of the valve piston of the torque control valve 106 is moved from its control position, so that the actuating chamber 102 pressure fluid flows or from the control chamber 102 pressure fluid can flow until another pivot angle is reached, in which again balance between the torques on Lever 1 15 prevails. Accordingly, if the hydraulic system pressure and thus the pressure in the line 103 increases, the valve piston of the torque control valve 106 is pulled to the right according to FIG. 2, whereby the system pressure is applied via the line 108 to the pivoting piston 76. This therefore reduces the inclination of the swash plate 43 to the torque balance on the lever arm 115. The output from the motor drive torque to the shaft 22 can thus be kept constant.

Claims

Patentansprüche claims
1. Hydraulischer Antrieb für einen hydraulischen Verbraucher (8) oder ein 1. Hydraulic drive for a hydraulic consumer (8) or a
Hydrauliksystem (4) mit einer verdrängungsvariablen Pumpe (2), die mechanisch mit einem drehzahlvariablen Antriebsmotor (10) gekoppelt ist und einer Steuerung (12) zur Verstellung des Hubvolumens der Pumpe (2), dadurch gekennzeichnet, dass die Pumpe (2) drehmomentgeregelt ist. Hydraulic system (4) with a variable displacement pump (2), which is mechanically coupled to a variable-speed drive motor (10) and a controller (12) for adjusting the stroke volume of the pump (2), characterized in that the pump (2) is torque-controlled ,
2. Hydraulischer Antrieb nach Anspruch 1 , gekennzeichnet durch eine Druck- erfassungs-/ oder -bestimmungseinrichtung zur Erfassung des aktuellen Drucks am Verbraucher (8) oder im Hydrauliksystem (4), wobei die Pumpe (2) derart eingestellt wird, dass die Gleichung T = konst = P x V gilt, wobei T(konst) = vorbestimmter Abgabedrehmomentwert des Antriebsmotors, P = Verbraucher-/Hydrauliksystemdruck und V = Hubvolumen der Pumpe. 2. Hydraulic drive according to claim 1, characterized by a pressure detection / or determination device for detecting the current pressure at the load (8) or in the hydraulic system (4), wherein the pump (2) is set such that the equation T = const = P x V, where T (const) = predetermined output torque value of the drive motor, P = load / hydraulic system pressure and V = stroke volume of the pump.
3. Hydraulischer Antrieb nach Anspruch 2, dadurch gekennzeichnet, dass die Pumpe (2) mit einem mechanisch-hydraulischen Drehmomentregler (106) ausgestattet ist. 3. Hydraulic drive according to claim 2, characterized in that the pump (2) is equipped with a mechanical-hydraulic torque controller (106).
4. Hydraulischer Antrieb nach einem der Patentansprüche 1 bis 3, dadurch gekennzeichnet, dass die Drehzahl des Antriebsmotors (10) in Abhängigkeit vom aktuellen Hubvolumen der Pumpe (2) so eingestellt wird, dass eine vorbestimmte Bewegungsgeschwindigkeit des hydraulischen Verbrauchers erhalten wird. 4. Hydraulic drive according to one of the claims 1 to 3, characterized in that the rotational speed of the drive motor (10) in dependence on the current displacement of the pump (2) is adjusted so that a predetermined movement speed of the hydraulic load is obtained.
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