EP1350033B1 - Device for the force oil feed of a hydraulic consumer operated at a defined operating pressure - Google Patents

Device for the force oil feed of a hydraulic consumer operated at a defined operating pressure Download PDF

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Publication number
EP1350033B1
EP1350033B1 EP02706702A EP02706702A EP1350033B1 EP 1350033 B1 EP1350033 B1 EP 1350033B1 EP 02706702 A EP02706702 A EP 02706702A EP 02706702 A EP02706702 A EP 02706702A EP 1350033 B1 EP1350033 B1 EP 1350033B1
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EP
European Patent Office
Prior art keywords
pressure
pump
oil
clamping
valve
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
EP02706702A
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German (de)
French (fr)
Other versions
EP1350033A2 (en
Inventor
Dieter Jordan
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Voith Turbo H and L Hydraulic GmbH and Co KG
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Voith Turbo H and L Hydraulic GmbH and Co KG
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • F15B1/027—Installations or systems with accumulators having accumulator charging devices
    • F15B1/033—Installations or systems with accumulators having accumulator charging devices with electrical control means
    • 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
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F15B15/26—Locking mechanisms
    • F15B2015/268—Fluid supply for locking or release independent of actuator pressurisation
    • 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
    • F15B2211/20576—Systems with pumps with multiple pumps
    • F15B2211/20584—Combinations of pumps with high and low 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
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/62—Cooling or heating means
    • 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
    • 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
    • F15B2211/6653—Pressure control

Definitions

  • the invention relates to a device for pressurized oil supply operated at a defined operating pressure p B hydraulic consumer, in whose operation a significant leakage oil flow occurs, which is returned to the reservoir of a pressure supply unit, and with the other, mentioned in the preamble of claim 1, generic determining features.
  • the pressure supply unit comprises a first, permanently in the sense of a charge as a pressure source for the consumer, eg. Example, a hydraulic clamping cylinder of a clamping device for a rotationally drivable, a rotatable submissible workpiece, used pressure accumulator working pump, and a second pump that feeds a cooling circuit in a virtually powerless circulation operation, in the hydraulic oil from the reservoir via an oil cooler back to the reservoir of the pressure supply unit is directed.
  • This oil cooling is the limitation of the temperature of the hydraulic oil to a value associated with a viscosity of the hydraulic oil suitable for the operation of the consumer, in which also a leakage oil flow, which may be due to a rotary union, is supplied to the consumer with pressurized oil within a limited range of values can be maintained so that the used for charging the pressure accumulator first pump must not be designed for a disproportionately high peak flow rate.
  • a memory charging device controlled by a pressure monitoring device is provided, by means of which, after falling off the memory pressure below a threshold p SU, the memory is rechargeable to a pressure p S , which is significantly higher than the operating pressure used in the consumer, the z. B. is adjustable by means of a consumer associated pressure setting valve.
  • the pressure supply unit also serves for short-term pressure oil supply at least one additional hydraulic consumer, z. B.
  • one of the turning processing station which comprises the clamping cylinder, associated tool changer, can be delivered to the various provided for the machining of the workpiece tools of the processing station, the - relatively short term - pressure oil demand of such additional consumer, based on the unit time, be significantly higher can be considered to be that of the consumer to be operated at a defined operating pressure p B whose operating pressure p B should be substantially constant over the turning machining time in order to ensure a good machining quality of the workpiece.
  • the permanently working in the sense of charging the pressure accumulator pump is designed as a swash plate axial piston pump, the delivery volume per rotor revolution is automatically adjustable adjustable.
  • the object of the invention is therefore to improve a device of the type mentioned in that at the same time simpler and cheaper construction of the same a significant reduction of the periods is achieved, within which the need-based pressure oil supply is reached.
  • the permanently pumping into the pressure accumulator first pump can be designed for a relatively low flow rate, which only has to be sufficient to compensate for the associated leakage caused by the associated consumer and maintain the accumulator pressure within a limited range at an average value p S , which is sufficient to derive therefrom the operating pressure p B of the consumer.
  • the permanently pumping into the memory pump can therefore be designed as a relatively small and correspondingly inexpensive fixed displacement pump.
  • the usually in almost powerless circulation operation promoting, the cooling circuit feeding pump is designed for a flow rate that corresponds to twice to three times the amount of capacity of the permanently operating in the loading pump.
  • an advantageous design of designed as a pressure-controlled valve accumulator charging valve is specified, which mediates a rapid and reliable switching of the normally feeding the cooling circuit pump in the storage loading operation.
  • pressure oil supply means for the total designated in Fig. 1 with 10 pressure oil supply means is merely for the purpose of explanation, ie without limitation of generality, provided that a hydraulic actuator a double-acting, linear hydraulic cylinder 11 is provided, for. B. the clamping cylinder of a hydraulic tensioning device 12 represented by this, not shown in the other lathe, said tensioning device 12 on the one hand clamping a z. B. round rod-shaped workpiece 13 "from the outside" or, on the other hand, a clamping of a z.
  • tubular workpiece 14 "from the inside” allows, and these alternative clamping functions of the clamping device 12 are associated with alternative directions of deflections of the tubular work spindle 16 on a portion of its length outside surrounding cylinder housing 17 relative to a spindle-fixed piston flange 18 through which within the Cylinder housing 17 two annular pressure chambers 19 and 21 are pressure-tight against each other delimited by the alternative pressurization and discharge the direction of deflection of the cylinder housing 17 can be predetermined and thus the type of Maschinen Swisseinnaps can be selected.
  • clamping device designed as a four-two-way solenoid valve, designated overall with 22 function control valve with latched functional positions I and II provided by alternative excitation of two control windings 23 and 24 of the switching magnet from the previously occupied switching position I and II in the alternative switching position II or I is switchable.
  • the consumer ports 28 and 31 of the function control valve 22 are provided via a provided on the clamping cylinder 11, a total of 34 rotary union and the pressure chambers 19 and 21 of the clamping cylinder 11 individually associated, integrated in the housing 17 and fixedly mounted on this pilot check valves 36 and 37th with one of the pressure chambers 19 and 21 hydraulically connected.
  • the two check valves 36 and 37 are controlled in their open position when the operating pressure P B is present at one of the consumer ports 28 or 31 of the function control valve 22, but arrive at a drop in operating pressure, ie when the p B supply port 27 of the function control valve pending pressure falls, in its blocking position, so that pressure oil from the pressure chambers 19 and 21 of the clamping cylinder 11 can not drain and the clamping function of the clamping device 12 is maintained at least for a safety period.
  • a clamping pressure setting valve 38 is provided between the pressure output 39 of the pressure supply unit 33 and the P B supply port 27 of the function control valve 22 is connected.
  • the pressure supply unit 33 comprises two (high) pressure pumps 41 and 42 which are connected via this individually associated pressure oil filter 77 and 78 and these downstream outlet check valves 43 and 44 to the pressure outlet 39 of the pressure supply unit 33.
  • the two pumps 41 and 42 have a common, electrically controlled drive motor 48 and are therefore, as long as it is driven, both in operation.
  • the pumps 41 and 42 are designed as constant pumps, whose related to the speed of the drive motor 48 flow rates Q 1 and Q 2 are different.
  • the output pressure level of the pressure supply unit 33 is connected by means of a pressure relief valve 49 which is connected between the pressure output 39 of the pressure supply unit 33 and the unpressurized reservoir 32, to a predetermined by adjusting the bias of a valve spring 51 of the pressure relief valve value p max of z. B. 90 bar limited.
  • a pressure accumulator 52 is connected, which is in case of malfunction of the pressure supply unit 33 as an "auxiliary" pressure source for a time-limited “safety” operation available, within which the working operation of a equipped with the clamping cylinder 11 processing machine can be switched off without the risk that the workpiece 13 or 14 is not clamped with sufficient certainty until the work spindle 16 is stopped.
  • This pressure accumulator 52 is dimensioned so that the memory contents sufficient, within the safety period, a pressure drop in each used pressure chamber 19 and 21 of the clamping cylinder, which is caused by a leakage oil, via the outgoing from the rotary feedthrough 34 leakage oil line 53 to the reservoir 32 of the pressure supply unit 33 is derived, so long as to compensate sufficiently, d. H. to ensure the firm clamping of the workpiece by means of the clamping device 12 until the drive spindle 16 is braked to a standstill.
  • the related to the speed of the drive motor 48 flow rate Q 1 of a pump 41 and thus firmly correlated flow Q 2 of the other Pump 42 of the pressure supply unit 33 are in a special design of the pressure oil supply device 10 in the ratio 1: 3 to each other.
  • a circulating flow path leading through the oil cooler 57 back to the reservoir 32 denoted overall by 58, branches off a pressure-controlled switching valve 59, which mediates the function of a storage charging valve, releasable and - if necessary - can be shut off.
  • the pressure supply unit 33 of the pressure oil supply device 10 is also provided to the pressure oil supply of another, only schematically indicated consumer 61 which is connected via a (high) pressure supply line 62 to the pressure output 39 of the pressure supply unit 33 and either via a separate return line or one with the return line 26th the pressure oil supply device 10 connected return line branch 26 'and via a separate or connected to the drain line 53 leak oil line branch 53' to the non-pressure reservoir 32 of the pressure supply unit 33 is connected
  • the clamping pressure setting valve 38 is designed so that by - manual or motor-driven - adjustment of the bias of its valve spring 65 of the operating pressure port 27 of the function control valve 22 provided operating pressure p B is adjustable within a wide range, eg. B. between 10% and 90% of the pressure output 39 provided at the output pressure p A of the pressure supply unit, which also corresponds to the pressure of the stored pressure in the accumulator 52 pressure oil.
  • This adjustability is the need-based adjustment of means the clamping device 12 achieved on the respective workpiece 13 or 14 clamping forces to the stability of the workpiece.
  • the change-over valve 59 which is used as a storage charge valve as needed, is designed so that, starting from an operating situation in which the output pressure p A present at the pressure output 39 of the pressure supply unit is greater than an upper switching threshold p SO , the z. B.
  • the accumulator charging valve 59 comprises a total of 59/1 designated switching valve unit and a total of 59/2 designated control unit.
  • the switching valve unit 59/1 comprises a cylindrical cup-shaped switching piston 81 which is guided in a pressure-tight manner in a housing bore 82 and in this housing bore a connection space 83, to which the pressure outlet 54 of "larger" pump 42 is connected, delimits against a control chamber 84, which in turn communicates with a control chamber 86 of the control unit 59/2 in communicating connection.
  • the terminal compartment 83 is connected via a arranged at the bottom of the cup-shaped piston 81 throttle bore 87 with the control chamber 84 in communicating connection, which in turn communicates via a correspondingly shaped throttle bore 88 with the control chamber 86 of the control unit 59/2 in communicating connection.
  • the control chamber is bounded on the housing side by two coaxial bores 91 and 92 adjoining one another via a radial shoulder 89.
  • a control piston 93 is guided pressure-tightly displaceable, which also forms the axially movable boundary of a pressure sensor chamber 94, in which the prevailing at the pressure outlet 39 and in the memory 52 pressure p A is coupled.
  • the annular transitional edge 96 between the smaller bore step 92 and a conical extension to a larger diameter bore step 97 forms a valve seat for a valve ball 98 which is urged against the valve seat 96 by a valve spring 99 with adjustable spring force F f .
  • the relief chamber 101 containing the valve spring 99 is connected to the reservoir 32 via a drain line 105.
  • the cross-sectional area A1 of the smaller bore step 92 which can be covered by the valve ball 48 is smaller than the cross-sectional area A2 of the larger bore 91 of the control unit 59/2 shut off by the cylindrical control piston 93.
  • the control piston 93 is supported on the valve ball 98 via a slender plunger 106.
  • the ball seat valve 96, 98 of the control unit 59/2 opens as soon as the force resulting from the fact that the valve ball 98 is exposed to the pressure p A on an effective area A1, is greater than the set bias of the spring 99.
  • the control chamber 86 relieved to the reservoir 32 toward, likewise the piston 81 of the Umschaltventiliser 59/1, whose piston against the restoring force of the weak return spring 102 reaches the open position of the Umschaltventiliser 59/1.
  • the pressure p su at which the control unit 59/2 returns to the blocking state of its ball seat valve, corresponding to the area ratio A 1 / A 2 is lower than the value p SO at which the ball seat valve 96/98 opens due to the injected into the control chamber 86 pressure.
  • an electronic or electromechanical pressure sensor 64 which generates an electrical output signal characteristic of the accumulator pressure or the pressure p A at the pressure output 39 of the pressure supply unit 33.
  • This output signal is only shown schematically, provided for operation control of the pressure oil supply device 10 provided electronic control unit 66, by the z. B manually take-off operation first, the drive motor 48 of the two pumps 41 and 42 is turned on, both working in the initial phase of the clamping operation both in terms of a rapid pressure build-up in the used for fixed voltage pressure chamber 21 of the clamping cylinder 11 and a correspondingly rapid charging of the pressure accumulator 52.
  • the upper switching threshold P SO at which the switching valve 59 automatically switches the larger pump 42 automatically to circulation mode, reaches the electronic control unit 66 on the basis of a temporal Processing - "observation” - the output signal of the pressure sensor 64 detects.
  • the electronic control unit 66 mediates the switching on of the drive motor of the work spindle 16 and other functions, the following explanation as can be considered sufficiently for the description of the electronic-circuit construction of the electronic control unit, the realization of which is expected by a person skilled in the electro-hydraulic circuit technology with knowledge of these functions due to common expertise.
  • the electronic control unit 66 reacts thereto with a drive of the pump drive motor 48 in the sense of increasing the engine speed and thus the flow rate of the two pumps 41 and 42.
  • the cooling effect increases, with the result that on the leakage oil line 53 to the reservoir 32 out flowing leakage oil flow is reduced and the pressure in the pressure accumulator 52 increases again, ultimately with the result that pressure fluctuations in the exploited for the clamping operation pressure chamber 21 or 19 of the clamping cylinder 11 are largely avoided.
  • the electronic control unit 66 As further inputs, which are processed by the electronic control unit according to plausibility criteria to drive signals for the drive motor 48 of the pumps 41 and 42, by the drive motor 48 is driven so that a switching of the switching valve 59 of cooling operation of the larger pump 42 on pressure generating operation of the same largely is avoided, the electronic control unit 66 on the one hand the electrical output signal of the electronic temperature sensor 67, which is a measure of the temperature in the reservoir 32 of the pressure supply unit 33, and on the other hand fed an electrical speed signal, which is a measure of the speed ⁇ , with the drive spindle 16 rotational is driven.
  • the temperature-characteristic output signal of the temperature sensor 67 is an indirect measure of the viscosity of the pressure oil with which the hydraulic consumer 11 is operated;
  • the speed characteristic input signal of the electronic control unit 66 which, depending on the type of drive motor of the drive spindle 16 can be obtained from its control or can be generated by a speed sensor 68 which directly detects the speed of the drive spindle 16, is an indirect measure of the thermal load of used to operate the consumer pressure oil and insofar as a measure of the likelihood that significant leakage oil flows occur, which can lead to a pressure drop in the consumer.
  • the electronic control unit If the temperature rises in the reservoir 32 of the pressure supply unit 33, which is detected by means of the temperature sensor 67 to, without simultaneously in the pressure accumulator 52, a significant pressure drop occurs, d. H. the capacity of the smaller pump 41 is sufficient to cover the pressure oil requirement of the clamping cylinder 11, the electronic control unit generates an output signal which increases the rotational speed of an electric drive motor 69 and thus the air flow of a merely schematically indicated cooling fan 71, which generates a cooling air flow to the trained as an oil-to-air heat exchanger oil cooler 57 is passed.
  • This type of temperature monitoring of the circulating in the device 10 pressure oil is useful in the event that the clamping device is operated with relatively low clamping forces, ie comparatively low pressure in each used pressure chamber 19 or 21 of the clamping cylinder 11, the work spindle 16, however, driven at high speed is, so that, due to the internal friction in the pressure oil, although a significant increase in temperature may occur, the leakage oil flow, however, remains relatively low because of the relatively low pressure gradient between the drive pressure chamber of the clamping cylinder 11 and the reservoir 32.
  • This type of oil temperature control is also appropriate in the event that the device 10 to the pressure oil supply to another consumer 71, z. B. a hydrostatic rotary bearing is used, which is to be operated with a temporally constant as possible oil flow.
  • the electronic control unit 66 provides in the event that the means 10 is provided for supplying pressurized oil to a plurality of electrically controllable consumers, also the order of their switching on and off, preferably so that the frequency of switching operations of the accumulator charging valve 59 is minimized.
  • the output 72 of the pressure relief valve 49 of the pressure supply unit 33 is connected directly to a drain pipe 73 leading to the reservoir 32, via which the pressure accumulator 52 can be emptied by manually opening a drain valve 75 which is shut off in the supply operation of the device 10 ,
  • a hydromechanical pressure gauge 74 is provided which, independently of activation of the electronic control unit 66, provides an indication of the accumulator pressure.
  • the outflow outlet 72 of the pressure limiting valve 49 is connected via a dashed drain line 76 to the circulation flow path 58 and thereby directly to the oil cooler 57.

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

Abstract

A pressure feed system has a first pump (41) permanently loading a pressure accumulator (52) used as a source of pressure for a hydraulic cylinder (11). A second pump (42) feeds a cooling circuit operating in a low power mode. A reservoir-loading configuration (RLC) (41,42,59) loads a reservoir up to a specific pressure when the reservoir pressure falls below a threshold value. The RLC has a switch valve to switch the second pump to a mode for reservoir loading.

Description

Die Erfindung betrifft eine Einrichtung zur Druckölversorgung eines mit einem definierten Betriebsdruck pB betriebenen hydraulischen Verbrauchers, in dessen Betrieb ein signifikanter Leckölstrom auftritt, der zum Vorratsbehälter eines Druckversorgungsaggregats zurückgeleitet ist, und mit den weiteren, im Oberbegriff des Patentanspruchs 1 genannten, gattungsbestimmenden Merkmalen.The invention relates to a device for pressurized oil supply operated at a defined operating pressure p B hydraulic consumer, in whose operation a significant leakage oil flow occurs, which is returned to the reservoir of a pressure supply unit, and with the other, mentioned in the preamble of claim 1, generic determining features.

Eine Einrichtung dieser Art ist durch die US-A 4,819,430 bekannt. Bei einer von der Anmelderin für den Einsatz bei Bearbeitungszentren konzipierten Einrichtung der eingangs genannten Art umfaßt das Druckversorgungsaggregat eine erste, permanent im Sinne einer Aufladung eines als Druckquelle für den Verbraucher, z. B. einen hydraulischen Spannzylinder einer Spannvorrichtung für ein rotatorisch antreibbares, einer Drehbearbeitung unterwerfbares Werkstück, genutzten Druckspeichers arbeitende Pumpe, sowie eine zweite Pumpe, die in einem nahezu leistungslosen Umlaufbetrieb einen Kühlkreislauf speist, in dem Hydrauliköl vom Vorratsbehälter über einen Ölkühler zurück zum Vorratsbehälter des Druckversorgungsaggregats geleitet wird. Zweck dieser Ölkühlung ist die Begrenzung der Temperatur des Hydrauliköls auf einen mit einer für den Betrieb des Verbrauchers geeigneten Viskosität des Hydrauliköls verknüpften Wert, bei dem auch ein Leckölstrom, der durch eine Drehdurchführung bedingt sein kann, Ober die der Verbraucher mit Drucköl versorgt wird, innerhalb eines begrenzten Wertebereiches gehalten werden kann, damit die zur Aufladung des Druckspeichers benutzte erste Pumpe nicht auf eine unverhältnismäßig hohe Spitzenförderleistung ausgelegt sein muß. Des weiteren ist eine von einer Drucküberwachungseinrichtung gesteuerte Speicherladeeinrichtung vorgesehen, mittels derer nach einem Abfallen des Speicherdruckes unter einen Schwellenwert pSU der Speicher wieder auf einen Druck pS aufladbar ist, der signifikant höher ist als der im Verbraucher genutzte Betriesbdruck, der z. B. mittels eines dem Verbraucher zugeordneten Druckvorgabeventils einstellbar ist. Das Druckversorgungsaggregat dient auch zur kurzzeitigen Druckölversorgung mindestens eines weiteren hydraulischen Verbrauchers, z. B. eines der Drehbearbeitungsstation, die den Spannzylinder umfaßt, zugeordneten Werkzeugwechslers, mit dem verschiedene für die Bearbeitung des Werkstückes vorgesehene Werkzeuge der Bearbeitungsstation zugestellt werden können, wobei der - relativ kurzzeitige - Druckölbedarf eines solchen zusätzlichen Verbrauchers, bezogen auf die Zeiteinheit, signifikant höher sein kann als derjenige des mit definiertem Betriebsdruck pB zu betreibenden Verbrauchers, dessen Betriebsdruck pB über die Drehbearbeitungszeit hinweg weitgehend konstant sein sollte, um eine gute Bearbeitungsqualität des Werkstücks zu sichern.A device of this kind is known from US-A 4,819,430. In one of the applicant for use in machining centers designed device of the type mentioned above, the pressure supply unit comprises a first, permanently in the sense of a charge as a pressure source for the consumer, eg. Example, a hydraulic clamping cylinder of a clamping device for a rotationally drivable, a rotatable submissible workpiece, used pressure accumulator working pump, and a second pump that feeds a cooling circuit in a virtually powerless circulation operation, in the hydraulic oil from the reservoir via an oil cooler back to the reservoir of the pressure supply unit is directed. The purpose of this oil cooling is the limitation of the temperature of the hydraulic oil to a value associated with a viscosity of the hydraulic oil suitable for the operation of the consumer, in which also a leakage oil flow, which may be due to a rotary union, is supplied to the consumer with pressurized oil within a limited range of values can be maintained so that the used for charging the pressure accumulator first pump must not be designed for a disproportionately high peak flow rate. Furthermore, a memory charging device controlled by a pressure monitoring device is provided, by means of which, after falling off the memory pressure below a threshold p SU, the memory is rechargeable to a pressure p S , which is significantly higher than the operating pressure used in the consumer, the z. B. is adjustable by means of a consumer associated pressure setting valve. The pressure supply unit also serves for short-term pressure oil supply at least one additional hydraulic consumer, z. B. one of the turning processing station, which comprises the clamping cylinder, associated tool changer, can be delivered to the various provided for the machining of the workpiece tools of the processing station, the - relatively short term - pressure oil demand of such additional consumer, based on the unit time, be significantly higher can be considered to be that of the consumer to be operated at a defined operating pressure p B whose operating pressure p B should be substantially constant over the turning machining time in order to ensure a good machining quality of the workpiece.

Damit der zeitweise signifikant erhöhte Druckölbedarf gedeckt werden kann, ist die permanent im Sinne der Aufladung des Druckspeichers arbeitende Pumpe als Schrägscheibenaxialkolbenpumpe ausgebildet, deren Fördervolumen pro Rotorumdrehung selbsttätig einstellbar veränderbar ist.Thus, the temporarily significantly increased pressure oil requirement can be met, the permanently working in the sense of charging the pressure accumulator pump is designed as a swash plate axial piston pump, the delivery volume per rotor revolution is automatically adjustable adjustable.

Die bekannte Einrichtung ist aufgrund ihrer insoweit erläuterten baulichen und funktionellen Eigenschaften mit zumindest den folgenden Nachteilen behaftet:The known device is subject to at least the following disadvantages due to its structural and functional properties explained so far:

Die bedarfsweise Einstellung der den Speicher aufladenden - ersten - Pumpe auf eine erhöhte Förderleistung nimmt wegen der hierbei zu beschleunigenden Massen, sei es im Sinne einer Erhöhung der Rotordrehzahl der Pumpe oder der Einstellung der Schrägscheibe gegen Rückstellkräfte, die durch die Pumpenkolben ausgeübt werden, verhältnismäßig viel Zeit in Anspruch, mit der Folge, daß in Fällen, in denen im Verlauf der Bearbeitung des Werkstückes mehrfach ein Werkzeugwechsel erforderlich ist, die hierfür insgesamt verbrauchte Zeit mit der Zeit vergleichbar wird, die das Werkstück der Bearbeitung unterworfen ist. Dies ist produktionstechnisch ungünstig, da die für den Werkzeugwechsel benötigten Zeitspannen in der Summe nach Möglichkeit deutlich kleiner sein sollten als die für die Bearbeitung des Werkstückes erforderliche Gesamtzeitspanne.The need for adjustment of the memory charging - first - pump to an increased capacity increases because of this case to be accelerated masses, either in terms of increasing the rotor speed of the pump or the adjustment of the swash plate against restoring forces exerted by the pump piston, relatively much Time to claim, with the result that in cases where a tool change is required several times during the processing of the workpiece, the purpose total consumed time becomes comparable with the time that the workpiece is subjected to machining. This is unfavorable in terms of production since the time intervals required for the tool change should, as far as possible, be significantly less than the total time span required for machining the workpiece.

Hiermit einhergehend ist auch nachteilig, daß die den Speicher permanent aufladende Pumpe auf eine relative große maximale Fördermenge ausgelegt sein muß, um im Werkzeugwechselbetrieb einen für eine einigermaße kurz gehaltene Wechselzeit hinreichend hohe Fördermenge liefern zu können. Der mit der Speicherladepumpe verknüpfte Bauaufwand und Raumbedarf ist daher relativ hoch und mit entsprechend hohen Kosten verknüpft.This is also associated with the disadvantage that the memory permanently charging pump must be designed for a relatively large maximum flow rate to deliver in tool change operation for a einigermaße short held change time sufficiently high flow rate can. The associated with the storage loading pump construction costs and space requirements is therefore relatively high and associated with correspondingly high costs.

Aufgabe der Erfindung ist es daher, eine Einrichtung der eingangs genannten Art dahingehend zu verbessern, daß bei gleichwohl einfacherem und preisgünstigerem Aufbau derselben eine signifikante Verkürzung der Zeitspannen erzielt wird, innerhalb derer die bedarfsgerechte Druckölversorgung erreichbar ist.The object of the invention is therefore to improve a device of the type mentioned in that at the same time simpler and cheaper construction of the same a significant reduction of the periods is achieved, within which the need-based pressure oil supply is reached.

Diese Aufgabe wird erfindungsgemäß durch die kennzeichnenden Merkmale des Patentanspruchs 1 gelöst. Hierdurch werden zumindest die folgenden Vorteile erzielt.This object is achieved by the characterizing features of claim 1. As a result, at least the following advantages are achieved.

Dadurch, daß die normalerweise zur Kühlung benutzte Pumpe schon im Förderbetrieb arbeitet, wenn sie bedarfsweise in den Speicherladebetrieb umgeschaltet wird, steht deren volle Förderleistung sofort zur Aufladung des Druckspeichers zur Verfügung, so daß sich, abgesehen von der Schaltzeit des Umschaltventils, die im Bereich einiger weniger Millisekunden liegt, praktisch keinerlei Verzögerung des Ladebetriebes ergibt und die zur Nachladung des Speichers benötigte Zeitspanne minimiert wird.The fact that the normally used for cooling pump already works in the conveying mode when it is switched, if necessary, in the accumulator charging mode, their full capacity is immediately available for charging the pressure accumulator available, so that, apart from the switching time of the switching valve, in the range of some less milliseconds, results in virtually no delay of the charging operation and the time required for recharging the memory is minimized.

Die permanent in den Druckspeicher fördernde erste Pumpe kann auf eine vergleichsweise geringe Förderleistung ausgelegt sein, die lediglich dafür ausreichend sein muß, den durch den zugeordneten Verbraucher bedingten Leckölstrom auszugleichen und den Speicherdruck innerhalb eines begrenzten Bereiches auf einem Mittelwert pS zu halten, der ausreichend ist, hiervon den Betriebsdruck pB des Verbrauchers abzuleiten. Die permanent in den Speicher fördernde Pumpe kann daher als eine relativ kleine und entsprechend preisgünstige Konstantpumpe ausgebildet sein.The permanently pumping into the pressure accumulator first pump can be designed for a relatively low flow rate, which only has to be sufficient to compensate for the associated leakage caused by the associated consumer and maintain the accumulator pressure within a limited range at an average value p S , which is sufficient to derive therefrom the operating pressure p B of the consumer. The permanently pumping into the memory pump can therefore be designed as a relatively small and correspondingly inexpensive fixed displacement pump.

Da die Zeitspannen, in denen die normalerweise zur Kühlung ausgenutzte Pumpe als Speicherladepumpe genutzt ist, deren Förderleistung sich zu derjenigen der permanent im Ladebetrieb arbeitenden Pumpe addiert, sehr kurz gehalten werden können, wird die Kühlwirkung nicht fühlbar beeinträchtigt, und es wird insgesamt trotz Reduktion des baulichen Aufwandes, insbesondere hinsichtlich der permanent im Ladebetrieb arbeitende Pumpe eine signifikante Verkürzung der Speicherladezeiten in Relation zu den für die Bearbeitung eines Werkstückes erforderlichen Bearbeitungszeiten erzielt.Since the periods in which the normally used for cooling exploited pump is used as a storage loading pump, whose capacity adds to that of the permanently operating in the pump charging mode, can be kept very short, the cooling effect is not felt impaired, and it is a total of despite reducing the Structural effort, in particular with regard to the pump operating permanently in the loading mode achieved a significant reduction of the storage loading times in relation to the processing times required for the machining of a workpiece.

In bevorzugter Gestaltung der erfindungsgemäßen Einrichtung ist die normalerweise im nahezu leistungslosen Umlaufbetrieb fördernde, den Kühlkreislauf speisende Pumpe auf eine Förderleistung ausgelegt, die dem doppelten bis dreifachen Betrag der Förderleistung der permanent im Ladebetrieb arbeitenden Pumpe entspricht.In a preferred embodiment of the device according to the invention, the usually in almost powerless circulation operation promoting, the cooling circuit feeding pump is designed for a flow rate that corresponds to twice to three times the amount of capacity of the permanently operating in the loading pump.

Durch die Merkmale des Anspruchs 3 ist eine vorteilhafte Auslegung eines als druckgesteuertes Ventil ausgebildeten Speicherladeventils angegeben, das eine rasche und zuverlässige Umschaltung der normalerweise den Kühlkreislauf speisenden Pumpe in deren Speicherladebetrieb vermittelt.Due to the features of claim 3, an advantageous design of designed as a pressure-controlled valve accumulator charging valve is specified, which mediates a rapid and reliable switching of the normally feeding the cooling circuit pump in the storage loading operation.

Unter Bedingungen, in denen während eines Bearbeitungsvorganges, insbesondere eines Feindrehvorganges, eine Umschaltung der zweiten, im Normalbetrieb der Einrichtung den Kühlkreislauf speisenden Pumpe nicht oder allenfalls sehr selten stattfinden sollte, ist es besonders zweckmäßig, wenn, entsprechend der bevorzugten Gestaltung der Einrichtung ein elektronischer oder elektromechanischer Drucksensor vorgesehen ist, der ein für den im Druckspeicher herrschenden Druck charakteristisches elektrisches Ausgangssignal erzeugt, so daß mindestens die erste Pumpe z. B. mittels einer die Ausgangssignale des Drucksensors verarbeitenden elektronischen Steuereinheit gemäß den Merkmalen des Anspruchs 4 ansteuerbar ist. Eine hiernach erfolgende Steuerung der Förderleistung der Pumpe erfolgt zweckmäßigerweise so, daß eine einmal eingesteuerte Erhöhung der Förderleistung so lange beibehalten wird, bis der Druckwert wieder erreicht wird, bei dem die Druckbegrenzung des Druckversorgungsaggregats, z. B. durch das Ansprechen eines Druckbegrenzungsventils, wirksam wird, was z. B. anhand der Ausgangssignale des Drucksensors erkennbar ist und eine hiernach wieder mögliche Reduzierung der Förderleistung der "druckgesteuerten" Pumpe in kleinen Schritten nur soweit erfolgt, daß der Speicherdruck nur geringfügig unterhalb des Ansprechwertes der Druckbegrenzung bleibt und auf jeden Fall oberhalb desjenigen Wertes gehalten wird, bei dem auch die zweite Pumpe in den Speicherladebetrieb umgeschaltet werden würde.Under conditions in which during a processing operation, in particular a fine turning operation, a switching of the second, in normal operation of the device the cooling circuit feeding pump should not or at most take place very rarely, it is particularly useful if, according to the preferred design of the device an electronic or electromechanical pressure sensor is provided which generates a characteristic of the pressure prevailing in the accumulator pressure electrical output signal, so that at least the first pump z. B. by means of the output signals of the pressure sensor processing electronic control unit according to the features of claim 4 is controllable. A hereinafter carried out controlling the flow rate of the pump is advantageously carried out so that a once initiated increase in the flow rate is maintained until the pressure value is reached again, in which the pressure limit of the pressure supply unit, z. B. by the response of a pressure relief valve, is effective, which z. B. on the basis of the output signals of the pressure sensor can be seen and thereafter again possible reduction of the delivery of the "pressure-controlled" pump in small steps only to the extent that the accumulator pressure remains only slightly below the threshold value of the pressure limit and is kept above that value in any case, in which the second pump would be switched to the storage loading operation.

Wenn die Förderleistung der permanent im Ladebetrieb arbeitenden ersten Pumpe erhöht wird, so ist es in aller Regel auch zweckmäßig, gleichsinnig die Förderleistung der zweiten, den Kühlkreislauf speisenden Pumpe zu erhöhen, da eine hierdurch bedingte Verbesserung der Kühlwirkung des Kühlkreislauf im Sinne einer Erhöhung bzw. Verringerung der Abnahme der Viskosität des Drucköls wirkt und damit im Ergebnis den Bedarf nach einer erhöhten Öleinspeisung in den Verbraucherkreislauf reduziert.When the delivery rate of the permanently operating in the loading mode first pump is increased, it is usually also appropriate to increase the capacity of the second, the cooling circuit feeding pump in the same direction, as a result of this conditional improvement of the cooling effect of the cooling circuit in terms of increasing or Reducing the decrease in the viscosity of the pressure oil acts and thus reduces the need for increased oil feed into the consumer cycle as a result.

Zum Zweck der einfachen Gestaltung des Druckversorgungsaggregats und der einfachen Steuerbarkeit der beiden Pumpen desselben sind diese in bevorzugter Gestaltung als Konstantpumpen ausgebildet, die einen gemeinsamen Antriebsmotor mit steuerbarer oder regelbarer Drehzahl haben.For the purpose of simple design of the pressure supply unit and the simple controllability of the two pumps of the same these are formed in a preferred design as fixed displacement pumps, which have a common drive motor with controllable or variable speed.

Alternativ oder zusätzlich zu einer Änderung der Förderleistung der permanent im Speicherladebetrieb arbeitenden ersten Pumpe und/oder der den Kühlkreislauf speisenden zweiten Pumpe in Abhängigkeit von erfaßten Druckwerten im Verbraucherkreis ist es auch vorteilhaft, wenn ein Temperatursensor vorgesehen ist, dessen Ausgangssignale zu einer Steuerung der Förderleistung des Druckversorgungsaggregats gemäß den Merkmalen des Anspruchs 7 ausnutzbar sind.Alternatively or in addition to a change in the delivery rate of the permanently operating in the storage loading mode first pump and / or the second circuit pumping the cooling circuit in response to detected pressure values in the load circuit, it is also advantageous if a temperature sensor is provided, the output signals to control the flow rate of the Pressure supply unit according to the features of claim 7 are exploitable.

Im Falle eines den Merkmalen des Anspruches 8 entsprechenden Einsatzes der erfindungsgemäßen Einrichtung zur Druckölversorgung eines hydraulischen Spannzylinders einer Drehmaschine ist es von besonderer Bedeutung, daß Speicherladevorgänge, die unter Ausnutzung der zweiten Pumpe erfolgen, nicht innerhalb der Zeitspannen stattfinden, in denen eine Feinbearbeitung des jeweiligen Werkstückes erfolgt, da ansonsten durch Ladevorgänge bedingte Druckschwankungen im Spannzylinder zu geringfügigen Änderungen der Spannkräfte in der Spannvorrichtung und dadurch zu sicht baren "Spuren" - irregulären Stellen - der bearbeitenden Werkstückoberfläche führen können.In case of the features of claim 8 corresponding use of the device according to the invention for pressurized oil supply of a hydraulic clamping cylinder of a lathe, it is of particular importance that storage loading operations that take place using the second pump does not take place within the periods in which a fine machining of the respective workpiece takes place, otherwise caused by charging pressure fluctuations in the clamping cylinder to minor changes in the clamping forces in the clamping device and thus to visible ble "traces" - irregular places - the machined workpiece surface can lead.

Es ist daher in einem solchen Einsatzfall besonders wichtig, alle Möglichkeiten der Betriebsdruckkonstanthaltung auszuschöpfen, bevor ein Speicherladevorgang unter Ausnutzung der den Kühlkreislauf speisenden Pumpe ausgelöst wird und daher zweckmäßig, wenn die Druckölversorgungseinrichtung mit einer Sensorik gemäß den Merkmalen des Anspruches 9 ausgestattet ist, wobei ein Temperatursensor dieser Sensorik zweckmäßigerweise zur Steuerung der Kühlleistung eines Ölkühlers, am einfachsten durchIt is therefore particularly important in such an application to exploit all possibilities of operating pressure maintenance before a storage charging operation is triggered by utilizing the cooling circuit feeding pump and therefore useful when the pressure oil supply device is equipped with a sensor according to the features of claim 9, wherein a temperature sensor this sensor conveniently for controlling the cooling capacity of an oil cooler, most simply by

Steuerung der Kühlluftförderleistung eines Kühllüfters ausgenutzt wird, der eine weitere Möglichkeit bietet, die Viskosität des Drucköls durch Kühlung relativ hoch zu halten und damit Druckabfällen im Verbraucherkreislauf entgegenzuwirken.Control of the cooling air flow capacity of a cooling fan is exploited, which offers a further possibility to keep the viscosity of the pressure oil by cooling relatively high and thus counteract pressure drops in the consumer circuit.

Zur Erzielung einer guten Kühlwirkung kann es auch vorteilhaft sein, einen Ausgangsölstrom des Druckbegrenzungsventils des Druckversorgungsaggregats direkt zum Ölkühler zu leiten, wie gemäß Anspruch 11 vorgesehen.To achieve a good cooling effect, it may also be advantageous to direct an output oil flow of the pressure relief valve of the pressure supply unit directly to the oil cooler, as provided according to claim 11.

Weitere Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung eines in der Zeichnung dargestellten, speziellen Ausführungsbeispiels. Es zeigen:

Fig. 1
ein schematisch vereinfachtes elektrohydraulisches Schaltbild einer erfindungsgemäßen Einrichtung zur Druckölversorgung eines zur Betätigung einer Spannvorrichtung einer Drehmaschine vorgesehenen hydraulischen Zylinders, der über eine Drehdurchführung an das Druckversorgungsaggregat der Hydraulikeinheit angeschlossen ist;
Fig. 2
Einzelheiten eines Speicherladeventils der Einrichtung gemäß Fig. 1.
Further details of the invention will become apparent from the following description of a particular embodiment shown in the drawing. Show it:
Fig. 1
a schematically simplified electro-hydraulic circuit diagram of a device according to the invention for pressurized oil supply of a hydraulic cylinder for actuating a clamping device of a lathe provided hydraulic cylinder which is connected via a rotary feedthrough to the pressure supply unit of the hydraulic unit;
Fig. 2
Details of a storage charging valve of the device according to FIG. 1.

Für die in Fig. 1 insgesamt mit 10 bezeichnete Druckölversorgungseinrichtung sei lediglich zum Zweck der Erläuterung, d. h. ohne Beschränkung der Allgemeinheit, vorausgesetzt, daß als hydraulischer Verbraucher ein doppelt wirkender, linearer Hydrozylinder 11 vorgesehen sei, z. B. der Spannzylinder einer hydraulischen Spannvorrichtung 12 einer durch diese repräsentierten, im übrigen nicht dargestellten Drehmaschine, wobei diese Spannvorrichtung 12 einerseits ein Spannen eines z. B. rundstabförmigen Werkstücks 13 "von außen" oder, andererseits, ein Spannen eines z. B. rohrförmigen Werkstückes 14 "von innen" ermöglicht, und wobei diesen alternativen Spannfunktionen der Spannvorrichtung 12 alternative Richtungen der Auslenkungen eines die rohrförmige Arbeitsspindel 16 auf einem Abschnitt ihrer Länge außenseitig umgebenden Zylindergehäuses 17 relativ zu einem spindelfesten Kolbenflansch 18 zugeordnet sind, durch den innerhalb des Zylindergehäuses 17 zwei ringförmige Druckräume 19 und 21 druckdicht gegeneinander abgegrenzt sind, durch deren alternative Druckbeaufschlagung und -entlastung die Richtung der Auslenkung des Zylindergehäuses 17 vorgebbar und damit die Art der Werkstückeinspannung wählbar ist.For the total designated in Fig. 1 with 10 pressure oil supply means is merely for the purpose of explanation, ie without limitation of generality, provided that a hydraulic actuator a double-acting, linear hydraulic cylinder 11 is provided, for. B. the clamping cylinder of a hydraulic tensioning device 12 represented by this, not shown in the other lathe, said tensioning device 12 on the one hand clamping a z. B. round rod-shaped workpiece 13 "from the outside" or, on the other hand, a clamping of a z. Example, tubular workpiece 14 "from the inside" allows, and these alternative clamping functions of the clamping device 12 are associated with alternative directions of deflections of the tubular work spindle 16 on a portion of its length outside surrounding cylinder housing 17 relative to a spindle-fixed piston flange 18 through which within the Cylinder housing 17 two annular pressure chambers 19 and 21 are pressure-tight against each other delimited by the alternative pressurization and discharge the direction of deflection of the cylinder housing 17 can be predetermined and thus the type of Werkstückeinspannung can be selected.

Zur Auswahl der werkstückgerechten Art der Einspannung, die mittels der Spannvorrichtung erzielt werden soll, ist ein als Vier-Zwei-Wegemagnetventil ausgebildetes, insgesamt mit 22 bezeichnetes Funktionssteuerventil mit gerasteten Funktionsstellungen I und II vorgesehen, das durch alternative Erregung zweier Steuerwicklungen 23 und 24 von Schaltmagneten aus der jeweils zuvor eingenommenen Schaltstellung I und II in die dazu alternative Schaltstellung II bzw. I umschaltbar ist.To select the workpiece-like type of clamping, which is to be achieved by means of the clamping device, designed as a four-two-way solenoid valve, designated overall with 22 function control valve with latched functional positions I and II provided by alternative excitation of two control windings 23 and 24 of the switching magnet from the previously occupied switching position I and II in the alternative switching position II or I is switchable.

In der einen Schaltstellung I des Funktionssteuerventils 22 ist dessen Betriebsdruck (pB)-Anschluß 27 mit dem A-Verbraucheranschluß 28 verbunden und der T-Rücklaufanschluß 29 mit dem B-Verbraucheranschluß 31 des Funktionssteuerventils 22 verbunden. In der anderen Funktionsstellung II des Funktionssteuerventils 22 ist dessen pB-Versorgungsanschluß mit dem B-Verbraucheranschluß 31 verbunden und der T-Rücklaufanschluß 29, von dem eine Rücklaufleitung 26 "direkt" zum drucklosen Vorratsbehälter 32 des insgesamt mit 33 bezeichneten Druckversorgungsaggregats führt, mit dem A-Verbraucheranschluß 28 des Funktionssteuerventils 22 verbunden.In one switching position I of the function control valve 22 whose operating pressure (p B ) connection 27 is connected to the A-consumer port 28 and the T-return port 29 to the B-consumer port 31 of the function control valve 22 is connected. In the other functional position II of the function control valve 22 whose p B supply port is connected to the B-consumer port 31 and the T-return port 29, of which a return line 26 "directly" leads to the unpressurized reservoir 32 of the total designated 33 pressure supply unit, with the A-consumer terminal 28 of the function control valve 22 connected.

Die Verbraucheranschlüsse 28 und 31 des Funktionssteuerventils 22 sind über eine an dem Spannzylinder 11 vorgesehene, insgesamt mit 34 bezeichnete Drehdurchführung und den Druckräumen 19 und 21 des Spannzylinders 11 einzeln zugeordnete, in dessen Gehäuse 17 integrierte bzw. an diesem fest montierte entsperrbare Rückschlagventile 36 und 37 mit je einem der Druckräume 19 bzw. 21 hydraulisch verbunden. Die beiden Rückschlagventile 36 und 37 sind in ihre Offenstellung gesteuert, wenn an einem der Verbraucheranschlüsse 28 oder 31 des Funktionssteuerventils 22 der Betriebsdruck PB ansteht, gelangen jedoch bei einem Abfall des Betriebsdruckes, d. h. wenn der am pB-Versorgungsanschluß 27 des Funktionssteuerventils anstehende Druck abfällt, in ihre Sperrstellung, so daß Drucköl aus den Druckkammern 19 und 21 des Spannzylinders 11 nicht abfließen kann und die Spannfunktion der Spannvorrichtung 12 zumindest für eine Sicherheitszeitspanne erhalten bleibt.The consumer ports 28 and 31 of the function control valve 22 are provided via a provided on the clamping cylinder 11, a total of 34 rotary union and the pressure chambers 19 and 21 of the clamping cylinder 11 individually associated, integrated in the housing 17 and fixedly mounted on this pilot check valves 36 and 37th with one of the pressure chambers 19 and 21 hydraulically connected. The two check valves 36 and 37 are controlled in their open position when the operating pressure P B is present at one of the consumer ports 28 or 31 of the function control valve 22, but arrive at a drop in operating pressure, ie when the p B supply port 27 of the function control valve pending pressure falls, in its blocking position, so that pressure oil from the pressure chambers 19 and 21 of the clamping cylinder 11 can not drain and the clamping function of the clamping device 12 is maintained at least for a safety period.

Zur Vorgabe des Betriebsdruckes pB, der je nach dem gewählten Spannmodus in den einen oder anderen Druckraum 19 oder 21 des Spannzylinders 11 zur Entfaltung der erforderlichen Spannkraft der Spannvorrichtung 12 eingekoppelt werden soll, ist ein Spanndruckvorgabeventil 38 vorgesehen, das zwischen den Druckausgang 39 des Druckversorgungsaggregats 33 und den PB-Versorgungsanschluß 27 des Funktionssteuerventils 22 geschaltet ist.To specify the operating pressure p B , which is to be coupled depending on the selected clamping mode in one or the other pressure chamber 19 or 21 of the clamping cylinder 11 for deployment of the required clamping force of the clamping device 12, a clamping pressure setting valve 38 is provided between the pressure output 39 of the pressure supply unit 33 and the P B supply port 27 of the function control valve 22 is connected.

Das Druckversorgungsaggregat 33 umfaßt zwei (Hoch)-Druckpumpen 41 und 42, die über diesen einzeln zugeordnete Druckölfilter 77 und 78 und diesen nachgeschaltete Ausgangsrückschlagventile 43 und 44 an den Druckausgang 39 des Druckversorgungsaggregats 33 angeschlossen sind.The pressure supply unit 33 comprises two (high) pressure pumps 41 and 42 which are connected via this individually associated pressure oil filter 77 and 78 and these downstream outlet check valves 43 and 44 to the pressure outlet 39 of the pressure supply unit 33.

Die beiden Pumpen 41 und 42 haben einen gemeinsamen, elektrisch gesteuerten Antriebsmotor 48 und sind daher, so lange dieser angesteuert ist, beide in Betrieb. Die Pumpen 41 und 42 sind als Konstantpumpen ausgebildet, deren auf die Drehzahl des Antriebsmotors 48 bezogene Fördermengen Q1 und Q2 verschieden sind.The two pumps 41 and 42 have a common, electrically controlled drive motor 48 and are therefore, as long as it is driven, both in operation. The pumps 41 and 42 are designed as constant pumps, whose related to the speed of the drive motor 48 flow rates Q 1 and Q 2 are different.

Das Ausgangsdruckniveau des Druckversorgungsaggregats 33 ist mittels eines Druckbegrenzungsventils 49, das zwischen den Druckausgang 39 des Druckversorgungsaggregats 33 und dessen drucklosen Vorratsbehälter 32 geschaltet ist, auf einen durch Einstellung der Vorspannung einer Ventilfeder 51 des Druckbegrenzungsventils vorgebbaren Wert pMax von z. B. 90 Bar begrenzt.The output pressure level of the pressure supply unit 33 is connected by means of a pressure relief valve 49 which is connected between the pressure output 39 of the pressure supply unit 33 and the unpressurized reservoir 32, to a predetermined by adjusting the bias of a valve spring 51 of the pressure relief valve value p max of z. B. 90 bar limited.

An den Druckausgang 39 des Druckversorgungsaggregats 33 ist ein Druckspeicher 52 angeschlossen, der im Falle einer Fehlfunktion des Druckversorgungsaggregats 33 als "Hilfs"-Druckquelle für einen zeitlich begrenzten "Sicherheits"-Betrieb nutzbar ist, innerhalb dessen der Arbeitsbetrieb einer mit dem Spannzylinder 11 ausgerüsteten Bearbeitungsmaschine abgeschaltet werden kann, ohne daß die Gefahr besteht, daß das Werkstück 13 bzw. 14 nicht mit hinreichender Sicherheit bis zum Stillstand der Arbeitsspindel 16 festgespannt bleibt.At the pressure output 39 of the pressure supply unit 33, a pressure accumulator 52 is connected, which is in case of malfunction of the pressure supply unit 33 as an "auxiliary" pressure source for a time-limited "safety" operation available, within which the working operation of a equipped with the clamping cylinder 11 processing machine can be switched off without the risk that the workpiece 13 or 14 is not clamped with sufficient certainty until the work spindle 16 is stopped.

Dieser Druckspeicher 52 ist so dimensioniert, daß der Speicherinhalt ausreicht, innerhalb der Sicherheitszeitspanne einen Druckabfall im jeweils genutzten Druckraum 19 bzw. 21 des Spannzylinders, der durch einen Leckölstrom bedingt ist, der über die von der Drehdurchführung 34 ausgehende Leckölleitung 53 zum Vorratsbehälter 32 des Druckversorgungsaggregats 33 abgeleitet ist, so lange hinreichend kompensieren zu können, d. h. die feste Einspannung des Werkstücks mittels der Spannvorrichtung 12 gewährleisten zu können, bis die Antriebsspindel 16 auf Stillstand abgebremst ist.This pressure accumulator 52 is dimensioned so that the memory contents sufficient, within the safety period, a pressure drop in each used pressure chamber 19 and 21 of the clamping cylinder, which is caused by a leakage oil, via the outgoing from the rotary feedthrough 34 leakage oil line 53 to the reservoir 32 of the pressure supply unit 33 is derived, so long as to compensate sufficiently, d. H. to ensure the firm clamping of the workpiece by means of the clamping device 12 until the drive spindle 16 is braked to a standstill.

Die auf die Drehzahl des Antriebsmotors 48 bezogene Fördermenge Q1 der einen Pumpe 41 und die damit fest korrelierte Fördermenge Q2 der anderen Pumpe 42 des Druckversorgungsaggregats 33 stehen in spezieller Auslegung der Druckölversorgungseinrichtung 10 im Verhältnis 1 : 3 zueinander.The related to the speed of the drive motor 48 flow rate Q 1 of a pump 41 and thus firmly correlated flow Q 2 of the other Pump 42 of the pressure supply unit 33 are in a special design of the pressure oil supply device 10 in the ratio 1: 3 to each other.

Zwischen dem Druckausgang 54 der auf die größere Fördermenge Q2 ausgelegten "größeren" Pumpe 42 und deren Ausgangsrückschlagventil 44 zweigt von dem Ausgangspfad 56 dieser Pumpe 42 ein über einen Ölkühler 57 zurück zum Vorratsbehälter 32 führender, insgesamt mit 58 bezeichneter, Umlaufströmungspfad ab, der mittels eines druckgesteuerten Umschaltventils 59, das die Funktion eines Speicherladeventils vermittelt, freigebbar und - bedarfsweise - absperrbar ist.Between the pressure output 54 of the "larger" pump 42 designed for the larger flow rate Q 2 and its outlet check valve 44, from the outlet path 56 of this pump 42, a circulating flow path leading through the oil cooler 57 back to the reservoir 32, denoted overall by 58, branches off a pressure-controlled switching valve 59, which mediates the function of a storage charging valve, releasable and - if necessary - can be shut off.

Das Druckversorgungsaggregat 33 der Druckölversorgungseinrichtung 10 ist auch zur Druckölversorgung eines weiteren, lediglich schematisch angedeuteten Verbrauchers 61 vorgesehen, der über eine (Hoch)-Druckversorgungsleitung 62 mit dem Druckausgang 39 des Druckversorgungsaggregats 33 verbunden ist und entweder über eine separate Rücklaufleitung oder einen mit der Rücklaufleitung 26 der Druckölversorgungseinrichtung 10 verbundenen Rücklaufleitungszweig 26' sowie über einen separaten oder mit der Leckölleitung 53 verbundenen Leckölleitungszweig 53' mit dem drucklosen Vorratsbehälter 32 des Druckversorgungsaggregats 33 verbunden istThe pressure supply unit 33 of the pressure oil supply device 10 is also provided to the pressure oil supply of another, only schematically indicated consumer 61 which is connected via a (high) pressure supply line 62 to the pressure output 39 of the pressure supply unit 33 and either via a separate return line or one with the return line 26th the pressure oil supply device 10 connected return line branch 26 'and via a separate or connected to the drain line 53 leak oil line branch 53' to the non-pressure reservoir 32 of the pressure supply unit 33 is connected

Das Spanndruckvorgabeventil 38 ist dahingehend ausgelegt, daß durch - manuelle oder motorisch gesteuerte - Einstellung der Vorspannung seiner Ventilfeder 65 der am Betriebsdruckanschluß 27 des Funktionssteuerventils 22 bereitgestellte Betriebsdruck pB innerhalb eines weiten Bereiches einstellbar ist, z. B. zwischen 10 % und 90 % des am Druckausgang 39 bereitgestellten Ausgangsdruckes pA des Druckversorgungsaggregats, dem auch der Druck des im Druckspeicher 52 gespeicherten Drucköls entspricht. Durch diese Einstellbarkeit wird die bedarfsgerechte Anpassung der mittels der Spannvorrichtung 12 auf das jeweilige Werkstück 13 oder 14 auszuübenden Spannkräfte an die Stabilität des Werkstückes erzielt.The clamping pressure setting valve 38 is designed so that by - manual or motor-driven - adjustment of the bias of its valve spring 65 of the operating pressure port 27 of the function control valve 22 provided operating pressure p B is adjustable within a wide range, eg. B. between 10% and 90% of the pressure output 39 provided at the output pressure p A of the pressure supply unit, which also corresponds to the pressure of the stored pressure in the accumulator 52 pressure oil. This adjustability is the need-based adjustment of means the clamping device 12 achieved on the respective workpiece 13 or 14 clamping forces to the stability of the workpiece.

Das bedarfsweise als Speicherladeventil genutzte Umschaltventil 59 ist dahingehend ausgelegt, daß es, ausgehend von einer Betriebssituation, in der der am Druckausgang 39 des Druckversorgungsaggregats anstehende Ausgangsdruck pA größer ist als ein oberer Umschaltschwellenwert pSO, der z. B. um 2 bis 3 % niedriger ist als der maximale Ausgangsdruck des Druckversorgungsaggregats 33, der dem durch das Druckbegrenzungsventil 49 vorgegebenen Wert entspricht, seine Durchflußstellung einnimmt, in der die der Fördermenge nach größere Pumpe 42 in dem zur Ölkühlung ausgenutzten, nahezu leistungslosen Umlaufbetrieb arbeitet, für den Fall, daß der Ausgangsdruck pA auf einen unteren Umschaltschwellenwert psu absinkt, der um etwa 5 bis 20 %, vorzugsweise 10 bis 15 % niedriger ist als der maximale Ausgangsdruck des Druckversorgungsaggregats, in seine Sperrstellung gelangt, in der auch die größere Pumpe 42 über ihr Ausgangsrückschlagventil 44 zur Druckversorgung des Spannzylinders 11 beiträgt und die Wiederaufladung des Druckspeichers 52 vermittelt, und, sobald der Ausgangsdruck pA wieder auf den oberen Umschaltschwellenwert pSO angestiegen ist, wieder in seine Durchflußstellung umschaltet, in der der Ausgangsölstrom der größeren Förderpumpe wieder zum Ölkühler 57 geleitet ist und die größere Ölpumpe 42 wieder im Umlaufbetrieb arbeitet.The change-over valve 59, which is used as a storage charge valve as needed, is designed so that, starting from an operating situation in which the output pressure p A present at the pressure output 39 of the pressure supply unit is greater than an upper switching threshold p SO , the z. B. is 2 to 3% lower than the maximum output pressure of the pressure supply unit 33, which corresponds to the predetermined value by the pressure relief valve 49, assumes its flow position, in which the flow rate for larger pump 42 in the used for oil cooling, almost powerless circulation operation works , in the event that the output pressure p A drops to a lower switching threshold p su , which is about 5 to 20%, preferably 10 to 15% lower than the maximum output pressure of the pressure supply unit, reaches its blocking position, in which also the larger Pump 42 contributes via its output check valve 44 to the pressure supply of the clamping cylinder 11 and the recharging of the pressure accumulator 52 mediates, and, as soon as the output pressure p A has risen again to the upper switching threshold p SO , again switches to its flow position, in the output oil flow of the larger feed pump back to the oil cooler 57 is directed and the larger oil pump 42 again works in circulation mode.

Zu einer mehr in die Einzelheiten gehenden Erläuterung des Speicherladeventils 59 hinsichtlich seines prinzipiellen Aufbaues und seiner Funktion sei nunmehr auf die Fig. 2 Bezug genommen. Das Speicherladeventil 59 umfaßt eine insgesamt mit 59/1 bezeichnete Umschaltventileinheit und eine insgesamt mit 59/2 bezeichnete Steuereinheit. Die Umschaltventileinheit 59/1 umfaßt einen zylindrisch topfförmigen Umschaltkolben 81, der in einer Gehäusebohrung 82 druckdicht verschiebbar geführt ist und in dieser Gehäusebohrung einen Anschlußraum 83, an den der Druckausgang 54 der "größeren" Pumpe 42 angeschlossen ist, gegen einen Steuerraum 84 abgrenzt, der seinerseits mit einer Steuerkammer 86 der Steuereinheit 59/2 in kommunizierender Verbindung steht. Der Anschlußraum 83 steht über eine am Boden des topfförmig gestalteten Kolbens 81 angeordnete Drosselbohrung 87 mit dem Steuerraum 84 in kommunizierender Verbindung, der seinerseits über eine entsprechend gestaltete Drosselbohrung 88 mit der Steuerkammer 86 der Steuereinheit 59/2 in kommunizierender Verbindung steht.For a more detailed explanation of the accumulator charging valve 59 in terms of its basic structure and function, reference is now made to FIG. The accumulator charging valve 59 comprises a total of 59/1 designated switching valve unit and a total of 59/2 designated control unit. The switching valve unit 59/1 comprises a cylindrical cup-shaped switching piston 81 which is guided in a pressure-tight manner in a housing bore 82 and in this housing bore a connection space 83, to which the pressure outlet 54 of "larger" pump 42 is connected, delimits against a control chamber 84, which in turn communicates with a control chamber 86 of the control unit 59/2 in communicating connection. The terminal compartment 83 is connected via a arranged at the bottom of the cup-shaped piston 81 throttle bore 87 with the control chamber 84 in communicating connection, which in turn communicates via a correspondingly shaped throttle bore 88 with the control chamber 86 of the control unit 59/2 in communicating connection.

Die Steuerkammer ist gehäuseseitig durch zwei über eine radiale Schulter 89 aneinander anschließende, koaxiale Bohrungen 91 und 92 begrenzt. In der dem Durchmesser nach größeren Bohrung 91 ist ein Steuerkolben 93 druckdicht verschiebbar geführt, der auch die axial bewegliche Begrenzung einer Drucksensorkammer 94 bildet, in die der am Druckausgang 39 bzw. im Speicher 52 herrschende Druck pA eingekoppelt ist. Die kreisringförmige Übergangskante 96 zwischen der kleineren Bohrungsstufe 92 und einer konischen Erweiterung zu einer Bohrungsstufe 97 größeren Durchmessers bildet einen Ventilsitz für eine Ventilkugel 98, die von einer Ventilfeder 99 mit einstellbarer Federkraft Ff gegen den Ventilsitz 96 gedrängt wird. Der die Ventilfeder 99 enthaltende Entlastungsraum 101 ist über eine Abflußleitung 105 mit dem Vorratsbehälter 32 verbunden.The control chamber is bounded on the housing side by two coaxial bores 91 and 92 adjoining one another via a radial shoulder 89. In the larger diameter bore 91, a control piston 93 is guided pressure-tightly displaceable, which also forms the axially movable boundary of a pressure sensor chamber 94, in which the prevailing at the pressure outlet 39 and in the memory 52 pressure p A is coupled. The annular transitional edge 96 between the smaller bore step 92 and a conical extension to a larger diameter bore step 97 forms a valve seat for a valve ball 98 which is urged against the valve seat 96 by a valve spring 99 with adjustable spring force F f . The relief chamber 101 containing the valve spring 99 is connected to the reservoir 32 via a drain line 105.

Die von der Ventilkugel 48 abdeckbare Querschnittsfläche A1 der kleineren Bohrungsstufe 92 ist kleiner als die durch den zylindrischen Steuerkolben 93 abgesperrte Querschnittsfläche A2 der größeren Bohrung 91 der Steuereinheit 59/2. Der Steuerkolben 93 ist über einen schlanken Stößel 106 an der Ventilkugel 98 abgestützt.The cross-sectional area A1 of the smaller bore step 92 which can be covered by the valve ball 48 is smaller than the cross-sectional area A2 of the larger bore 91 of the control unit 59/2 shut off by the cylindrical control piston 93. The control piston 93 is supported on the valve ball 98 via a slender plunger 106.

Zur Erläuterung der Funktion des insoweit einem speziellen Aufbau nach erweiterten Speicherladeventils 59 sei von einer Situation der Inbetriebnahme der Druckölversorgungseinrichtung 10 ausgegangen, in der die Ventilkugel 98 dichtend auf den Sitz 96 gedrängt ist und der Kolben 81 der Umschaltventileinheit 59/1 durch eine schwache Rückstellfeder 102 in die Sperrstellung des Ventils gedrängt ist, in der der Anschlußraum 83 gegen den Ausgangskanal 103, an den z. B. der Kühler 57 gemäß Fig. 1 angschlossen ist, abgesperrt ist. Mit dem Ansteigen des Druckes pA am Ausgang 39, dem im wesentlichen auch der in den Steuerraum 84 der Umschaltventileinheit 59/1 und in die Steuerkammer 86 der Steuereinheit 59/2 eingekoppelte Druck entspricht, sind die auf den Steuerkolben 93 wirkenden druckbedingten Kräfte zunächst ausgeglichen.To explain the function of the extent to a special structure for extended accumulator charging valve 59 is assumed to be a situation of commissioning the pressure oil supply device 10 in which the valve ball 98 is sealingly urged onto the seat 96 and the piston 81 of the changeover valve unit 59/1 is urged by a weak return spring 102 in the blocking position of the valve, in which the terminal space 83 against the output channel 103, to the z. B. the cooler 57 is connected as shown in FIG. 1, is shut off. With the increase in the pressure p A at the output 39, which also corresponds to the injected into the control chamber 84 of the switching valve 59/1 and 59 in the control chamber 86 of the control unit 59/2, the pressure acting on the control piston 93 pressure-related forces are initially balanced ,

Das Kugelsitzventil 96, 98 der Steuereinheit 59/2 öffnet, sobald die Kraft, die daraus resultiert, daß die Ventilkugel 98 auf einer wirksamen Fläche A1 dem Druck pA ausgesetzt ist, größer ist als die eingestellte Vorspannung der Feder 99. Mit dem Öffnen dieses Kugelsitzventils wird die Steuerkammer 86 zum Vorratsbehälter 32 hin entlastet, desgleichen der Kolben 81 der Umschaltventileinheit 59/1, deren Kolben gegen die Rückstellkraft der schwachen Rückstellfeder 102 in die Offenstellung der Umschaltventileinheit 59/1 gelangt.The ball seat valve 96, 98 of the control unit 59/2 opens as soon as the force resulting from the fact that the valve ball 98 is exposed to the pressure p A on an effective area A1, is greater than the set bias of the spring 99. By opening this Ball seat valve, the control chamber 86 relieved to the reservoir 32 toward, likewise the piston 81 of the Umschaltventileinheit 59/1, whose piston against the restoring force of the weak return spring 102 reaches the open position of the Umschaltventileinheit 59/1.

Bedingt durch den Unterschied der Flächen A1 und A2 ist der Druck psu, bei dem die Steuereinheit 59/2 wieder in den sperrenden Zustand ihres Kugelsitzventils gelangt, entsprechend dem Flächenverhältnis A1/A2 niedriger als der Wert pSO, bei dem das Kugelsitzventil 96/98 aufgrund des in die Steuerkammer 86 eingekoppelten Druckes öffnet.Due to the difference of the areas A1 and A2, the pressure p su , at which the control unit 59/2 returns to the blocking state of its ball seat valve, corresponding to the area ratio A 1 / A 2 is lower than the value p SO at which the ball seat valve 96/98 opens due to the injected into the control chamber 86 pressure.

Zur Erläuterung der Funktion der insoweit nunmehr ihrem Aufbau nach beschriebenen Druckölversorgungseinrichtung 10 sei davon ausgegangen, daß das Funktionssteuerventil 22 schon in seine dem vorgesehenen Spannmodus, zugeordnete Funktionsstellung, z. B. die Funktionsstellung 1, geschaltet ist, des weiteren der hierfür mit Druck zu beaufschlagende Druckraum 21 des Spannzylinders 11 und der Druckspeicher 52 noch drucklos sind, demgemäß das Speicherladeventil 59 seine Sperrstellung einnimmt und die Einleitung des Festspannvorgangs durch Einschalten des Antriebsmotors 48 der beiden Pumpen 41 und 42 erfolgt.To explain the function of the extent now described their structure according to the pressure oil supply device 10, it is assumed that the function control valve 22 already in its intended clamping mode, associated functional position, for. B. the functional position 1, is connected, further of this with pressure to be acted upon pressure chamber 21 of the clamping cylinder 11 and the pressure accumulator 52 are still depressurized, accordingly, the accumulator charging valve 59 assumes its blocking position and the initiation of the clamping operation by switching on the drive motor 48 of the two pumps 41 and 42 takes place.

In diesem angenommenen Ausgangszustand der Druckölversorgungseinrichtung 10 darf der - nicht dargestellte - Antriebsmotor der Antriebsspindel 16 nicht aktivierbar sein, da die Spannvorrichtung 12 noch keinerlei Spannkraft entfaltet.In this assumed initial state of the pressure oil supply device 10 may not be activated - not shown - drive motor of the drive spindle 16, since the clamping device 12 still does not develop any clamping force.

Zur Erkennung dieses Zustandes ist ein elektronischer oder elektromechanischer Drucksensor 64 vorgesehen, der ein für den Speicherdruck bzw. den am Druckausgang 39 des Druckversorgungsaggregats 33 herrschenden Druck pA charakteristisches elektrisches Ausgangssignal erzeugt. Dieses Ausgangssignal ist einer lediglich schematisch dargestellten, zur Betriebssteuerung der Druckölversorgungseinrichtung 10 vorgesehenen elektronischen Steuereinheit 66 zugeleitet, durch deren z. B manuell erfolgende Einschaltbetätigung zunächst der Antriebsmotor 48 der beiden Pumpen 41 und 42 eingeschaltet wird, die in dieser Anfangsphase des Spannbetriebes beide im Sinne eines raschen Druckaufbaus in dem zur Festspannung benutzten Druckraum 21 des Spannzylinders 11 sowie zu einer entsprechend raschen Aufladung des Druckspeichers 52 arbeiten.In order to detect this condition, an electronic or electromechanical pressure sensor 64 is provided which generates an electrical output signal characteristic of the accumulator pressure or the pressure p A at the pressure output 39 of the pressure supply unit 33. This output signal is only shown schematically, provided for operation control of the pressure oil supply device 10 provided electronic control unit 66, by the z. B manually take-off operation first, the drive motor 48 of the two pumps 41 and 42 is turned on, both working in the initial phase of the clamping operation both in terms of a rapid pressure build-up in the used for fixed voltage pressure chamber 21 of the clamping cylinder 11 and a correspondingly rapid charging of the pressure accumulator 52.

In dieser einleitenden "Spann"-Betriebsphase der Druckölversorgungseinrichtung 10 wird in der Regel schon nach kurzer Zeit der obere Umschaltschwellenwert PSO, bei dem das Umschaltventil 59 die größere Pumpe 42 selbsttätig druckgesteuert auf Umlaufbetrieb umschaltet, erreicht, was die elektronische Steuereinheit 66 anhand einer zeitlichen Verarbeitung - "Beobachtung" - des Ausgangssignals des Drucksensors 64 erkennt.In this introductory "clamping" operating phase of the pressure oil supply device 10, the upper switching threshold P SO , at which the switching valve 59 automatically switches the larger pump 42 automatically to circulation mode, reaches the electronic control unit 66 on the basis of a temporal Processing - "observation" - the output signal of the pressure sensor 64 detects.

Im weiteren Betrieb der Druckölversorgungseinrichtung 10 vermittelt die elektronische Steuereinheit 66 das Einschalten des Antriebsmotors der Arbeitsspindel 16 und weitere Funktionen, deren nachfolgende Erläuterung als ausreichend für die Beschreibung des elektronisch-schaltungstechnischen Aufbaus der elektronischen Steuereinheit angesehen werden kann, dessen Realisierung von einem Fachmann der elektrohydraulischen Schaltungstechnik bei Kenntnis dieser Funktionen aufgrund gängigen Fachwissens zu erwarten ist.In further operation of the pressure oil supply device 10, the electronic control unit 66 mediates the switching on of the drive motor of the work spindle 16 and other functions, the following explanation as can be considered sufficiently for the description of the electronic-circuit construction of the electronic control unit, the realization of which is expected by a person skilled in the electro-hydraulic circuit technology with knowledge of these functions due to common expertise.

Solche Funktionen sind mehr im einzelnen die folgenden:Such functions are more specifically the following:

Sinkt im Verlauf einer länger dauernden Bearbeitung des Werkstückes 13 oder 14 der Druck PS im Druckspeicher 52 mit mäßiger Änderungsrate ab, so reagiert die elektronische Steuereinheit 66 hierauf mit einer Ansteuerung des Pumpenantriebsmotors 48 im Sinne einer Erhöhung der Motordrehzahl und damit der Förderleistung der beiden Pumpen 41 und 42. Hierdurch wird durch Vergrößerung des Ölstromes, der über den Umlaufströmungspfad 58 durch den Kühler 57 geleitet wird, dessen Kühlwirkung erhöht, mit der Folge, daß ein über die Leckölleitung 53 zum Vorratsbehälter 32 hin abströmender Leckölstrom reduziert wird und der Druck im Druckspeicher 52 wieder ansteigt, letztlich mit der Folge, daß Druckschwankungen in dem für den Spannbetrieb ausgenutzten Druckraum 21 oder 19 des Spannzylinders 11 weitestgehend vermieden werden.Decreases in the course of a prolonged machining of the workpiece 13 or 14 of the pressure P S in the pressure accumulator 52 with moderate rate of change, the electronic control unit 66 reacts thereto with a drive of the pump drive motor 48 in the sense of increasing the engine speed and thus the flow rate of the two pumps 41 and 42. In this way, by increasing the flow of oil, which is passed through the circulating flow path 58 through the radiator 57, the cooling effect increases, with the result that on the leakage oil line 53 to the reservoir 32 out flowing leakage oil flow is reduced and the pressure in the pressure accumulator 52 increases again, ultimately with the result that pressure fluctuations in the exploited for the clamping operation pressure chamber 21 or 19 of the clamping cylinder 11 are largely avoided.

Als weitere Eingaben, die von der elektronischen Steuereinheit nach Plausibilitätskriterien zu Ansteuersignalen für den Antriebsmotor 48 der Pumpen 41 und 42 verarbeitet werden, durch die der Antriebsmotor 48 so angesteuert wird, daß eine Umschaltung des Umschaltventils 59 von Kühlbetrieb der größeren Pumpe 42 auf Druckerzeugungsbetrieb derselben weitgehend vermieden wird, sind der elektronischen Steuereinheit 66 zum einen das elektrische Ausgangssignal des elektronischen Temperatursensors 67, das ein Maß für die Temperatur im Vorratsbehälter 32 des Druckversorgungsaggregats 33 ist, und zum anderen ein elektrisches Drehzahlsignal zugeleitet, das ein Maß für die Drehzahl ν ist, mit der die Antriebsspindel 16 rotatorisch angetrieben ist. Das temperaturcharakteristische Ausgangssignal des Temperatursensors 67 ist ein indirektes Maß für die Viskosität des Drucköls, mit dem der hydraulischer Verbraucher 11 betrieben wird; das drehzahlcharakteristische Eingangssignal der elektronischen Steuereinheit 66, das, je nach Typ des Antriebsmotors der Antriebsspindel 16 aus dessen Ansteuerung gewonnen werden kann oder mittels eines Drehzahlsensors 68 generierbar ist, der direkt die Drehzahl der Antriebsspindel 16 erfaßt, ist ein indirektes Maß für die thermische Belastung des zum Betrieb des Verbrauchers benutzten Drucköls und insofern ein Maß für die Wahrscheinlichkeit, daß nennenswerte Leckölströme auftreten, die zu einem Druckabfall im Verbraucher führen können.As further inputs, which are processed by the electronic control unit according to plausibility criteria to drive signals for the drive motor 48 of the pumps 41 and 42, by the drive motor 48 is driven so that a switching of the switching valve 59 of cooling operation of the larger pump 42 on pressure generating operation of the same largely is avoided, the electronic control unit 66 on the one hand the electrical output signal of the electronic temperature sensor 67, which is a measure of the temperature in the reservoir 32 of the pressure supply unit 33, and on the other hand fed an electrical speed signal, which is a measure of the speed ν, with the drive spindle 16 rotational is driven. The temperature-characteristic output signal of the temperature sensor 67 is an indirect measure of the viscosity of the pressure oil with which the hydraulic consumer 11 is operated; the speed characteristic input signal of the electronic control unit 66, which, depending on the type of drive motor of the drive spindle 16 can be obtained from its control or can be generated by a speed sensor 68 which directly detects the speed of the drive spindle 16, is an indirect measure of the thermal load of used to operate the consumer pressure oil and insofar as a measure of the likelihood that significant leakage oil flows occur, which can lead to a pressure drop in the consumer.

Steigt die Temperatur im Vorratsbehälter 32 des Druckversorgungsaggregats 33, die mittels des Temperatursensors 67 erfaßt wird, an, ohne daß gleichzeitig im Druckspeicher 52 ein nennenswerter Druckabfall auftritt, d. h. die Förderleistung der kleineren Pumpe 41 ausreicht, den Druckölbedarf des Spannzylinders 11 zu decken, so erzeugt die elektronische Steuereinheit ein Ausgangssignal, das die Drehzahl eines elektrischen Antriebsmotors 69 und damit die Luftförderleistung eines lediglich schematisch angedeuteten Kühllüfters 71 erhöht, der einen Kühlluftstrom erzeugt, der zu dem als Öl-an-Luft-Wärmetauscher ausgebildeten Ölkühler 57 geleitet ist.If the temperature rises in the reservoir 32 of the pressure supply unit 33, which is detected by means of the temperature sensor 67 to, without simultaneously in the pressure accumulator 52, a significant pressure drop occurs, d. H. the capacity of the smaller pump 41 is sufficient to cover the pressure oil requirement of the clamping cylinder 11, the electronic control unit generates an output signal which increases the rotational speed of an electric drive motor 69 and thus the air flow of a merely schematically indicated cooling fan 71, which generates a cooling air flow to the trained as an oil-to-air heat exchanger oil cooler 57 is passed.

Diese Art der Temperaturüberwachung des in der Einrichtung 10 zirkulierenden Drucköls ist für den Fall zweckmäßig, daß die Spannvorrichtung mit relativ geringen Spannkräften, d. h. vergleichsweise geringem Druck im jeweils genutzten Druckraum 19 oder 21 des Spannzylinders 11 betrieben wird, die Arbeitsspindel 16 jedoch mit hoher Drehzahl angetrieben ist, so daß, bedingt durch die innere Reibung im Drucköl zwar eine erhebliche Temperaturerhöhung eintreten kann, der Leckölstrom jedoch wegen des relativ geringen Druckgefälles zwischen dem Antriebsdruckraum des Spannzylinders 11 und dem Vorratsbehälter 32 vergleichsweise gering bleibt.This type of temperature monitoring of the circulating in the device 10 pressure oil is useful in the event that the clamping device is operated with relatively low clamping forces, ie comparatively low pressure in each used pressure chamber 19 or 21 of the clamping cylinder 11, the work spindle 16, however, driven at high speed is, so that, due to the internal friction in the pressure oil, although a significant increase in temperature may occur, the leakage oil flow, however, remains relatively low because of the relatively low pressure gradient between the drive pressure chamber of the clamping cylinder 11 and the reservoir 32.

Diese Art der Öltemperaturregelung ist auch für den Fall zweckmäßig, daß die Einrichtung 10 zur Druckölversorgung eines weiteren Verbrauchers 71, z. B. eines hydrostatischen Drehlagers ausgenutzt ist, das mit einem zeitlich möglichst konstanten Ölstrom betrieben werden soll.This type of oil temperature control is also appropriate in the event that the device 10 to the pressure oil supply to another consumer 71, z. B. a hydrostatic rotary bearing is used, which is to be operated with a temporally constant as possible oil flow.

Die elektronische Steuereinheit 66 vermittelt für den Fall, daß die Einrichtung 10 zur Druckölversorgung mehrerer elektrisch ansteuerbarer Verbraucher vorgesehen ist, auch die Reihenfolge ihres Ein- und Ausschaltens, vorzugsweise so, daß die Häufigkeit von Umschaltvorgängen des Speicherladeventils 59 minimiert wird.The electronic control unit 66 provides in the event that the means 10 is provided for supplying pressurized oil to a plurality of electrically controllable consumers, also the order of their switching on and off, preferably so that the frequency of switching operations of the accumulator charging valve 59 is minimized.

Bei dem in der Zeichnung durch ausgezogene Linien repräsentierten Ausführungsbeispiel ist der Ausgang 72 des Druckbegrenzungsventils 49 des Druckversorgungsaggregats 33 direkt mit einer zum Vorratsbehälter 32 führenden Abflußleitung 73 verbunden, über die durch manuelles Öffnen eines im Versorgungsbetrieb der Einrichtung 10 gesperrten Ablaßventils 75 der Druckspeicher 52 entleerbar ist. Zur "visuellen" Kontrolle der Entladung des Druckspeichers 52 ist ein hydromechanisches Manometer 74 vorgesehen, das unabhängig von einer Aktivierung der elektronischen Steuereinheit 66 eine Anzeige des Speicherdruckes vermittelt.In the embodiment represented by solid lines in the drawing, the output 72 of the pressure relief valve 49 of the pressure supply unit 33 is connected directly to a drain pipe 73 leading to the reservoir 32, via which the pressure accumulator 52 can be emptied by manually opening a drain valve 75 which is shut off in the supply operation of the device 10 , For "visual" control of the discharge of the pressure accumulator 52, a hydromechanical pressure gauge 74 is provided which, independently of activation of the electronic control unit 66, provides an indication of the accumulator pressure.

Gemäß einer zweckmäßigen Abwandlung der Druckölversorgungseinrichtung 10 ist der Abflußausgang 72 des Druckbegrenzungsventils 49 über eine gestrichelt eingezeichnete Abflußleitung 76 mit dem Umlaufströmungspfad 58 und dadurch unmittelbar dem Ölkühler 57 verbunden.According to an expedient modification of the pressure oil supply device 10, the outflow outlet 72 of the pressure limiting valve 49 is connected via a dashed drain line 76 to the circulation flow path 58 and thereby directly to the oil cooler 57.

Gemäß einer weiteren Abwandlung der Druckölversorgungseinrichtung 10 ist anstelle der beiden Druckölfilter 77 und 78, die unmittelbar an die Druckausgänge der Pumpen 41 und 42 angeschlossen sind, nur ein einziges Druckölfilter 79 vorgesehen, das zwischen den Druckausgang 39 des Druckversorgungsaggregats 33 und das Spanndruckvorgabeventil 38 geschaltet ist.According to a further modification of the pressure oil supply device 10, instead of the two pressure oil filters 77 and 78, which are connected directly to the pressure outputs of the pumps 41 and 42, only a single pressure oil filter 79 is provided which between the pressure outlet 39 of the Compressor unit 33 and the clamping pressure setting valve 38 is connected.

Claims (11)

  1. Device for supplying pressure oil to a hydraulic consumer (11), in operation of which a significant flow of leaked oil occurs, and also for temporarily supplying pressure oil to at least one further hydraulic consumer (61), with a pressure supply aggregate (33), comprising a first pump (41), operating permanently in the sense of charging a pressure store (52) of the device for supplying pressure oil, used as a pressure source for the consumers (11, 61), and a second, permanently operating pump (42), and with a store-charging device (41, 42, 49), controlled by a pressure monitoring device (59, 64) of the device for supplying pressure oil and by means of which the pressure store (52) can be charged to a pressure pS, which is significantly higher than the operating pressure PB used in the consumer, wherein
    (a) the first pump (41) is designed for a discharge which is adequate to cover a preset amount of the flow of leaked oil linked to the operation of one of the hydraulic consumers (11) and to keep the storage pressure within a permissible variation range at a value pS to which an adequate stability of a defined operating pressure pB required by the consumer (11), is linked, characterised in that
    (b) the second pump (42) feeds a cooling circuit of the device for supplying pressure oil, in which, in virtually discharge-less circulating operation of the pump (42), hydraulic oil flows from a storage tank (32) of the pressure supply aggregate back to the storage tank via an oil cooler (57), in that
    (c) the storage charging device comprises a pressure-controlled switchover valve (59; 59/1, 59/2) which, in the event of a fall in the storage pressure to below a lower switchover threshold value pSU, switches the second pump (42) into a charging operation, in which this pump also provides the charging of the pressure store (52) and the pressure supply to the consumer (11) and, after the pressure store has been charged to a significantly higher switchover threshold value pSO again, switches the second pump back to circulating operation, in that
    (d) both pumps (41) and (42) are configured as constant pumps and in that
    (e) the second pump (42) is designed for a significantly higher discharge than the first pump.
  2. Device according to claim 1, characterised in that the second pump has a discharge corresponding to twice or three times the amount of the discharge of the first pump (41).
  3. Device according to claim 1 or claim 2, characterised in that the switchover valve (59) is constructed as a pressure-controlled valve, the lower switchover threshold value pSU of which, on going below which it provides the switchover of the second pump (42) from circulating operation to charging operation, is 5% to 20% lower than the maximum output pressure of the pressure supply aggregate (33), which is preset by setting a pressure-limiting valve (49) of the pressure supply aggregate(33), and the upper switchover threshold value pSO of which, on exceeding of which the switchover valve (59) switches the second pump (42) back into its circulating operation, is 1% to 3% lower than the maximum output pressure of the pressure supply aggregate (33).
  4. Device according to one of claims 1 to 3, characterised in that at least the first pump (41) is actuatable, in accordance with the output signal of an electronic or electromagnetic pressure sensor (64) of the device for supplying pressure oil, in such a way that with falling pressure in the consumer circuit the discharge of the first pump (41) increases to compensate.
  5. Device according to claim 4, characterised in that with a change in the discharge of the first pump (41) the discharge of the second pump (42) also changes in the same direction.
  6. Device according to claim 5, characterised in that the two pumps (41 and 42) are constructed as constant pumps driven by a common electric motor (48) of the pressure supply aggregate (33) at a speed controllable by open-loop or closed-loop control.
  7. Device according to one of claims 4 to 6, characterised in that an electronic or electromechanical temperature sensor (67) is provided, which generates an electric output signal, preferably characteristic of the temperature of the hydraulic oil in the storage tank, and in that an electronic control unit (66) responding to this output signal is provided, which introduces an increase in the discharge of at least the first pump (41) in monotonic relationship with a rise in the oil temperature.
  8. Device according to one of claims 1 to 7, usable for supplying pressure oil to a hydraulic clamping cylinder (11), with which a clamping device (12) is activatable, by means of which a workpiece can be fixed non-rotatably on an operating spindle (16) of a machine tool, drivable by rotary drive, wherein
    (a) the piston of the clamping cylinder is connected non-rotatably to the operating spindle (16) and the pressure coupling takes place into a pressure chamber (19 or 21) of the clamping cylinder (11), used in each case for clamping - external or internal clamping - of the clamping device (12), via a hydraulic rotary transmission leadthrough (34), furthermore
    (b) to preset the operating pressure pB required by the clamping cylinder (11), a clamping pressure preset valve (38) is provided, constructed as a pressure-reducing valve with adjustable output pressure pB, and
    (c) a function control valve (22), preferably electrically actuatable, with latched function settings (I and II) allocated to the alternative clamping operating states - external and internal clamping - of the clamping cylinder (11) or the clamping device (12) is switched between the clamping pressure preset valve (38) and the clamping cylinder (11).
  9. Device according to claim 8, characterised in that an electronic control unit is provided, which automatically sets the discharge of at least the first pump (41) and preferably both pumps (41 and 42) as a function of the operating temperature, the spindle speed and the clamping force of the clamping cylinder, preferably in the sense of a linear overlapping of the correcting variables allocated to these parameters.
  10. Device according to one of claims 1 to 9, characterised in that the oil cooler (57) comprises a cooling fan (71) with controllable cool air discharge.
  11. Device according to one of claims 1 to 10, characterised in that the output (72) of a pressure-limiting valve (49) provided to preset a maximum output pressure of the pressure supply aggregate (33) is connected to a circulating flow path (58) which connects the circulating valve (59) to the oil cooler (27).
EP02706702A 2001-01-12 2002-01-14 Device for the force oil feed of a hydraulic consumer operated at a defined operating pressure Expired - Lifetime EP1350033B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10101481 2001-01-12
DE10101481 2001-01-12
PCT/EP2002/000275 WO2002055886A2 (en) 2001-01-12 2002-01-14 Device for the force oil feed of a hydraulic consumer operated at a defined operating pressure p¿b?

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EP1350033A2 EP1350033A2 (en) 2003-10-08
EP1350033B1 true EP1350033B1 (en) 2007-02-14

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EP02706702A Expired - Lifetime EP1350033B1 (en) 2001-01-12 2002-01-14 Device for the force oil feed of a hydraulic consumer operated at a defined operating pressure

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EP (1) EP1350033B1 (en)
AT (1) ATE354030T1 (en)
DE (2) DE10201183A1 (en)
WO (1) WO2002055886A2 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2022990B1 (en) 2007-08-07 2016-10-12 HAWE Hydraulik SE Machine tool and supply unit
DE102012002224A1 (en) * 2012-02-04 2013-08-08 Hydac Cooling Gmbh Valve
CN106122130B (en) * 2016-07-08 2018-09-28 江苏元利数控机床有限公司 The control method of the fixture hydraulic device of pressure controllable
CN107504015B (en) * 2017-10-10 2024-04-05 宁波创力液压机械制造有限公司 Cable tension testing device
WO2020076199A1 (en) * 2018-10-08 2020-04-16 Saab Ab A multirod fluid actuator arrangement
CN113931728B (en) * 2021-01-19 2023-03-28 吉利汽车研究院（宁波）有限公司 Oil vapor control method, device and system and storage medium

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Publication number Priority date Publication date Assignee Title
US2745253A (en) * 1950-04-01 1956-05-15 Electraulic Presses Ltd Combined admission, relief and unloading valve and hydraulic power system
US4114637A (en) * 1976-12-20 1978-09-19 Double A Products Company Variable differential pressure unloading valve apparatus
US4819430A (en) * 1983-01-21 1989-04-11 Hydreco, Inc. Variably charged hydraulic circuit
DD215129A1 (en) * 1983-05-12 1984-10-31 Orsta Hydraulik Veb K POWER-CONTROLLED PRESSURE MEMORY SYSTEMS FOR HYDRAULIC DRIVES
DE19925665B4 (en) * 1999-06-04 2005-03-24 Zf Sachs Ag Method for adjusting the system pressure in a hydraulic actuator and hydraulic actuator

Also Published As

Publication number Publication date
EP1350033A2 (en) 2003-10-08
DE50209473D1 (en) 2007-03-29
WO2002055886A2 (en) 2002-07-18
WO2002055886A3 (en) 2003-01-09
ATE354030T1 (en) 2007-03-15
DE10201183A1 (en) 2002-08-14

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