WO2002055886A2 - Dispositif d'alimentation en huile sous pression destine a un consommateur hydraulique fonctionnant avec une pression de fonctionnement pb definie - Google Patents

Dispositif d'alimentation en huile sous pression destine a un consommateur hydraulique fonctionnant avec une pression de fonctionnement pb definie Download PDF

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Publication number
WO2002055886A2
WO2002055886A2 PCT/EP2002/000275 EP0200275W WO02055886A2 WO 2002055886 A2 WO2002055886 A2 WO 2002055886A2 EP 0200275 W EP0200275 W EP 0200275W WO 02055886 A2 WO02055886 A2 WO 02055886A2
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WO
WIPO (PCT)
Prior art keywords
pressure
pump
valve
reservoir
oil
Prior art date
Application number
PCT/EP2002/000275
Other languages
German (de)
English (en)
Other versions
WO2002055886A3 (fr
Inventor
Dieter Jordan
Original Assignee
Hartmann + Lämmle Gmbh & Co. Kg
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=7670551&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=WO2002055886(A2) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Hartmann + Lämmle Gmbh & Co. Kg filed Critical Hartmann + Lämmle Gmbh & Co. Kg
Priority to DE50209473T priority Critical patent/DE50209473D1/de
Priority to EP02706702A priority patent/EP1350033B1/fr
Publication of WO2002055886A2 publication Critical patent/WO2002055886A2/fr
Publication of WO2002055886A3 publication Critical patent/WO2002055886A3/fr

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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 supplying pressurized oil to a hydraulic consumer operated with a defined operating pressure p B , in the operation of which a significant leakage oil flow occurs, which is returned to the reservoir of a pressure supply unit, and with the further generic features mentioned in the preamble of claim 1.
  • the pressure supply unit comprises a first one, permanently in the sense of charging a pressure source for the consumer, e.g.
  • a pressure source for the consumer e.g.
  • a hydraulic clamping cylinder of a clamping device for a rotatably drivable workpiece that can be subjected to turning e.g.
  • a pressure accumulator used e.g.
  • a second pump that feeds a cooling circuit in an almost inefficient circulation mode, in which hydraulic oil from the reservoir via an oil cooler back to the reservoir of the pressure supply unit is directed.
  • This oil cooling is to limit the temperature of the hydraulic oil to a value linked to a viscosity of the hydraulic oil that is suitable for the operation of the consumer, at which a leakage oil flow, which may be caused by a rotating union, via which the consumer is supplied with pressurized oil , can be kept within a limited range of values so that the first pump used to charge the pressure accumulator does not have to be designed for a disproportionately high peak delivery rate.
  • a storage charging device controlled by a pressure monitoring device is provided, by means of which, after a if the storage pressure falls below a threshold value p S u the storage can be recharged to a pressure p s which is significantly higher than the operating pressure used in the consumer, which, for. B.
  • the pressure supply unit also serves for the short-term supply of pressure oil to at least one other hydraulic consumer, eg. B. one of the turning station, which includes the clamping cylinder, assigned tool changer, with which various tools provided for the machining of the workpiece can be delivered to the processing station, the - relatively short-term - pressure oil requirement of such an additional consumer, based on the unit of time, being significantly higher can be that of the consumer to be operated with a defined operating pressure p B , the operating pressure p B of which should be largely constant over the turning machining time in order to ensure good machining quality of the workpiece.
  • the pump which operates permanently in the sense of charging the pressure accumulator, is designed as a swash plate axial piston pump, the delivery volume of which can be changed automatically per revolution of the rotor.
  • the pump permanently charging the accumulator must be designed for a relatively large maximum delivery rate in order to be able to supply a sufficiently high delivery rate for a reasonably short changeover time in tool changing operation.
  • the construction costs and space requirements associated with the storage tank charging pump are therefore relatively high and are associated with correspondingly high costs.
  • the object of the invention is therefore to improve a device of the type mentioned in such a way that with a simpler and less expensive construction of the same, a significant reduction in the time periods within which the need-based pressure oil supply can be achieved is achieved.
  • the pump which is normally used for cooling, is already working in the delivery mode when it is switched to the storage tank charging mode, its full delivery rate is immediately available for charging the pressure accumulator, so that, apart from the switching time of the changeover valve, there are some is a few milliseconds, there is practically no delay in the charging operation and the time required to recharge the memory is minimized.
  • the first pump delivering permanently into the pressure accumulator can be designed for a comparatively low delivery rate, which only has to be sufficient to compensate for the leakage oil flow caused by the assigned consumer and to keep the accumulator pressure within a limited range at an average value p s that it is sufficient to derive the operating pressure p B of the consumer from this.
  • the pump that permanently pumps into the reservoir can therefore be designed as a relatively small and correspondingly inexpensive constant pump.
  • the pump which is normally used for cooling
  • the delivery capacity of which is added to that of the pump that is permanently in charging operation can be kept very short, the cooling effect is not noticeably impaired and, despite the reduction in, the overall structural effort, in particular with regard to the pump that is permanently operating in the loading mode, a significant reduction in the store loading times in relation to the machining times required for machining a workpiece.
  • the pump which feeds the cooling circuit and which is normally in almost no-load circulating operation is designed for a delivery rate which corresponds to twice or three times the amount of the delivery rate of the pump operating permanently in charging mode.
  • the features of claim 3 provide an advantageous design of a pressure control valve designed as a store loading valve, which provides a quick and reliable switchover of the pump that normally feeds the cooling circuit to its store loading operation.
  • a switching of the second pump, which feeds the cooling circuit during normal operation of the device should not take place, or at most very rarely, should take place during a machining process, in particular a fine turning process.
  • an electronic or Electromechanical pressure sensor is provided which generates a characteristic for the pressure prevailing in the pressure accumulator electrical output signal, so that at least the first pump z. B. can be controlled by means of an electronic control unit processing the output signals of the pressure sensor according to the features of claim 4.
  • a subsequent control of the delivery rate of the pump is expediently carried out so that a once increased increase in delivery rate is maintained until the pressure value is reached again, at which the pressure limitation of the pressure supply unit, for. B. by the response of a pressure relief valve, what z. B. is recognizable from the output signals of the pressure sensor and a subsequent possible reduction in the delivery rate of the "pressure-controlled" pump takes place in small steps only to such an extent that the storage pressure remains only slightly below the response value of the pressure limitation and in any case is kept above that value is, in which the second pump would also be switched to the storage charging mode.
  • the delivery rate of the first pump which is permanently operating in charging mode
  • these are designed in a preferred design as constant pumps which have a common drive motor with a controllable or adjustable speed.
  • the pressure oil supply device is equipped with a sensor system according to the features of claim 9, whereby a temperature sensor of this sensor system expediently to control the cooling capacity of an oil cooler, most simply by Control of the cooling air delivery capacity of a cooling fan is used, which offers a further possibility to keep the viscosity of the pressure oil relatively high by cooling and thus to counteract pressure drops in the consumer circuit.
  • FIG. 1 shows a schematically simplified electrohydraulic circuit diagram of a device according to the invention for supplying pressure oil to a hydraulic cylinder provided for actuating a clamping device of a lathe, which is connected to the pressure supply unit of the hydraulic unit via a rotary leadthrough;
  • FIG. 2 shows details of a storage loading valve of the device according to FIG. 1.
  • a double-acting, linear hydraulic cylinder 11 is provided as the hydraulic consumer, e.g. B. the clamping cylinder of a hydraulic clamping device 12 of a lathe represented by it, otherwise not shown, this clamping device direction 12 on the one hand a tensioning of a z.
  • a function control valve designated as a four-two-way solenoid valve and designated as a whole with 22 and with latched function positions I and II, is provided, which by alternative excitation of two control windings 23 and 24 of switching magnets can be switched from the previously assumed switching positions I and II to the alternative switching positions II and I, respectively.
  • the consumer connections 28 and 31 of the function control valve 22 are individually assigned via a rotary feedthrough provided on the tensioning cylinder 11, generally designated 34, and the pressure chambers 19 and 21 of the tensioning cylinder 11, which can be integrated into the housing 17 thereof or can be permanently attached to the latter and can be securely mounted thereon hydraulically connected to one of the pressure chambers 19 or 21.
  • the two non-return valves 36 and 37 are controlled in their open position when the operating pressure p B is present at one of the consumer connections 28 or 31 of the function control valve 22, but reach when the operating pressure drops, ie when the supply connection 27 of the function control valve at p B current pressure drops into its blocking position, so that pressure oil cannot flow out of the pressure chambers 19 and 21 of the tensioning cylinder 11 and the tensioning function of the tensioning device 12 is maintained at least for a safety period.
  • a clamping pressure specification valve 38 is provided, which is located between the pressure outlet 39 of the pressure supply unit 33 and the p B supply connection 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 to the pressure outlet 39 of the pressure supply unit 33 via these individually assigned pressure oil filters 77 and 78 and downstream check valves 43 and 44.
  • the two pumps 41 and 42 have a common, electrically controlled drive motor 48 and are therefore in operation as long as it is activated.
  • the pumps 41 and 42 are designed as constant pumps. det whose flow rates Q] and Q 2 are different based on the speed of the drive motor 48.
  • the output pressure level of the pressure supply unit 33 is by means of a pressure relief valve 49, which is connected between the pressure outlet 39 of the pressure supply unit 33 and its non-pressurized reservoir 32, to a value p Max of z, which can be predetermined by setting the preload of a valve spring 51 of the pressure relief valve. B. 90 bar limited.
  • a pressure accumulator 52 is connected to the pressure outlet 39 of the pressure supply unit 33 and, in the event of a malfunction of the pressure supply unit 33, can be used as an "auxiliary" pressure source for a time-limited "safety” mode, within which the working mode of a processing machine equipped with the clamping cylinder 11 can be used can be switched off without the risk that the workpiece 13 or 14 does not remain securely clamped until the work spindle 16 comes to a standstill.
  • This pressure accumulator 52 is dimensioned so that the storage content is sufficient, within the safety period, a pressure drop in the respective pressure chamber 19 or 21 of the clamping cylinder, which is caused by a leakage oil flow, which via the leakage oil line 53 originating from the rotary union 34 to the reservoir 32 of the pressure supply unit 33 is derived to be able to compensate sufficiently for so long, d. H. to be able to ensure the fixed clamping of the workpiece by means of the clamping device 12 until the drive spindle 16 is braked to a standstill.
  • the delivery rate Qi of one pump 41 related to the speed of the drive motor 48 and the delivery rate Q 2 of the other which is correlated with it Pump 42 of the pressure supply unit 33 are in a special design of the pressure oil supply device 10 in a ratio of 1: 3 to each other.
  • the pressure supply unit 33 of the pressure oil supply device 10 is also provided for the pressure oil supply to a further, only schematically indicated, consumer 61, which is connected via a (high) pressure supply line 62 to the pressure outlet 39 of the pressure supply unit 33 and either via a separate return line or one with the return line 26 the return line branch 26 'connected to the pressure oil supply device 10 and to the unpressurized reservoir 32 of the pressure supply unit 33 via a separate leak oil line branch 53' or connected to the leak oil line 53.
  • the clamping pressure specification valve 38 is designed in such a way that the operating pressure p B provided at the operating pressure connection 27 of the function control valve 22 can be adjusted within a wide range by - manual or motor-controlled - adjustment of the bias of its valve spring 65, e.g. B. between 10% and 90% of the output pressure p A provided at the pressure outlet 39 of the pressure supply unit, which also corresponds to the pressure of the pressure oil stored in the pressure accumulator 52.
  • This adjustability enables the need-based adjustment of the means the clamping device 12 on the respective workpiece 13 or 14 clamping forces to be achieved on the stability of the workpiece.
  • the changeover valve 59 used as a store loading valve is designed such that, starting from an operating situation in which the outlet pressure p A present at the pressure outlet 39 of the pressure supply unit is greater than an upper changeover threshold value p S o, the z. B. is 2 to 3% lower than the maximum outlet pressure of the pressure supply unit 33, which corresponds to the value given by the pressure relief valve 49, assumes its flow position in which the pump 42, which is larger in terms of the delivery rate, in the oil cooling, almost powerless Recirculation mode works, in the event that the outlet pressure p A falls to a lower changeover threshold p S u, which is about 10 to 15% lower than the maximum outlet pressure of the pressure supply unit, reaches its blocking position, in which the larger pump 42 contributes via its output check valve 44 to the pressure supply of the tensioning cylinder 11 and mediates the recharge of the pressure accumulator 52, and, as soon as the output pressure p A has risen again to the upper switching threshold value p S o, switches back to its flow position in which the output oil
  • the accumulator loading valve 59 comprises a switching valve unit, generally designated 59/1, and a control unit, generally designated 59/2.
  • the changeover valve unit 59/1 comprises a cylindrical pot-shaped changeover piston 81, which is displaceably 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 the "Larger" pump 42 is connected, delimited from a control chamber 84, which in turn communicates with a control chamber 86 of the control unit 59/2.
  • connection chamber 83 communicates with the control chamber 84 via a throttle bore 87 arranged on the bottom of the pot-shaped piston 81, which in turn communicates with the control chamber 86 of the control unit 59/2 via a correspondingly designed throttle bore 88.
  • the control chamber is delimited on the housing side by two coaxial bores 91 and 92 adjoining one another via a radial shoulder 89.
  • a control piston 93 is displaceably guided in a pressure-tight manner and also forms the axially movable boundary of a pressure sensor chamber 94, into which the pressure p A prevailing at the pressure outlet 39 or in the accumulator 52 is coupled.
  • the annular transition edge 96 between the smaller bore step 92 and a conical extension to a bore step 97 of larger diameter 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 that 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 which is blocked off by the cylindrical control piston 93.
  • the control piston 93 is supported on the valve ball 98 via a slim plunger 106.
  • the accumulator charging valve 59 which has a special design in this respect, a situation in which the pressure oil supply device 10 is started up is assumed, in which the valve ball 98 is pressed onto the seat 96 in a sealing manner and the piston 81 of the switching valve unit 59/1 is pushed by a weak return spring 102 into the blocking position of the valve, in which the connection space 83 against the output channel 103, to the z. B. the cooler 57 is connected according to FIG. 1, is shut off.
  • the ball seat valve 96, 98 of the control unit 59/2 opens as soon as the force resulting from the valve ball 98 being exposed to the pressure p A on an effective area A1 is greater than the set preload of the spring 99. With the opening thereof Ball seat valve relieves the pressure on the control chamber 86 towards the reservoir 32, as does the piston 81 of the changeover valve unit 59/1, the piston of which reaches the open position of the changeover valve unit 59/1 against the restoring force of the weak return spring 102.
  • the drive motor of the drive spindle 16 (not shown) must not be able to be activated, since the clamping device 12 does not yet develop any clamping force.
  • an electronic or electromechanical pressure sensor 64 which generates an electrical output signal characteristic of the accumulator pressure or the pressure p A prevailing at the pressure outlet 39 of the pressure supply unit 33.
  • This output signal is fed to an electronic control unit 66, which is shown only schematically and is provided for operating control of the pressure oil supply device 10.
  • the drive motor 48 of the two pumps 41 and 42 is first switched on, both of which work in this initial phase of the tensioning operation in the sense of a rapid build-up of pressure in the pressure space 21 of the tensioning cylinder 11 used for fixed tensioning and for a correspondingly rapid charging of the pressure accumulator 52.
  • the upper switching threshold value pso at which the switching valve 59 automatically switches the larger pump 42 to circulation mode under pressure control, is usually reached after a short time, which the electronic control unit 66 uses on the basis of time processing - "Observation” - the output signal of the pressure sensor 64 recognizes.
  • the electronic control unit 66 mediates the switching on of the drive motor of the work spindle 16 and further functions, the following explanation of which sufficient for the description of the electronic circuitry of the electronic control unit can be viewed, the implementation of which can be expected from a specialist in electrohydraulic circuitry with knowledge of these functions based on current specialist knowledge.
  • the electronic control unit 66 reacts to this by actuating the pump drive motor 48 in the sense of increasing the motor speed and thus the delivery capacity of the two pumps 41 and 42.
  • This increases the cooling effect by increasing the oil flow which is passed through the circulation flow path 58 through the cooler 57, with the result that a leakage oil flow flowing through the leakage oil line 53 to the reservoir 32 is reduced and the pressure in the pressure accumulator 52 rises again, ultimately with the result that pressure fluctuations in the pressure space 21 or 19 of the clamping cylinder 11 used for the clamping operation are largely avoided.
  • the electronic control unit 66 is supplied on the one hand with 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 with an electrical speed signal, which is a measure for the speed v at which the drive spindle 16 is rotatory 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 1 is operated;
  • the speed-characteristic input signal of the electronic control unit 66 which, depending on the type of drive motor, the drive spindle 16 can be obtained from its control or can be generated by means of a speed sensor 68 which directly detects the speed of the drive spindle 16, is an indirect measure of the thermal load on the pressure oil used to operate the consumer and, in this respect, a measure of the probability that significant leakage oil flows occur which can lead to a pressure drop in the consumer.
  • the electronic control unit If the temperature in the reservoir 32 of the pressure supply unit 33, which is detected by means of the temperature sensor 67, rises without an appreciable pressure drop occurring simultaneously in the pressure accumulator 52, i. H. If the delivery rate of the smaller pump 41 is sufficient to cover the pressure oil requirement of the tensioning cylinder 11, the electronic control unit generates an output signal which increases the speed of an electric drive motor 69 and thus the air delivery rate of a cooling fan 71, which is only indicated schematically and which generates a cooling air flow. which is directed to the oil cooler 57 designed as an oil-to-air heat exchanger.
  • This type of temperature monitoring of the pressure oil circulating in the device 10 is expedient in the event that the clamping device is operated with relatively low clamping forces, ie comparatively low pressure in the pressure chamber 19 or 21 of the clamping cylinder 11 used in each case, but the work spindle 16 is driven at high speed is, so that, due to the internal friction in the pressure oil, a considerable temperature increase can occur, however, the leakage oil flow remains comparatively low due to the relatively small pressure drop between the drive pressure chamber of the tensioning cylinder 11 and the reservoir 32.
  • This type of oil temperature control is also useful in the event that the device 10 for supplying pressure oil to another consumer 71, for. B. a hydrostatic rotary bearing is used, which is to be operated with a time constant oil flow.
  • the electronic control unit 66 also conveys the sequence in which it is switched on and off, preferably in such a way that the frequency of switching processes of the accumulator charging valve 59 is minimized.
  • the outlet 72 of the pressure limiting valve 49 of the pressure supply unit 33 is connected directly to a drain line 73 leading to the reservoir 32, via which the pressure accumulator 52 can be emptied by manually opening a drain valve 75 which is blocked in the supply operation of the device 10 ,
  • a hydromechanical manometer 74 is provided which, independently of an activation of the electronic control unit 66, provides an indication of the accumulator pressure.
  • the drain outlet 72 of the pressure limiting valve 49 is connected to the circulating flow path 58 and thus directly to the oil cooler 57 via a dashed-line drain line 76.
  • Pressure oil filter 79 provided between the pressure outlet 39 of the Pressure supply device 33 and the clamping pressure setting valve 38 ge ⁇ is switched on.

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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

La présente invention concerne un dispositif d'alimentation en huile sous pression destiné à un cylindre de serrage hydraulique (11) fonctionnant avec une pression de fonctionnement pB définie. Un flux d'huile de fuite important intervient dans le fonctionnement de serrage de ce cylindre de serrage et est reconduit au réservoir (32) d'une unité d'alimentation en pression (33) qui est également exploitée pour une alimentation en huile sous pression temporaire d'au moins un autre consommateur hydraulique. Ladite unité d'alimentation en pression comprend une première pompe (41) qui travaille de façon permanente à la charge d'un accumulateur de pression (52) servant de source de pression au consommateur (11; 61), ainsi qu'une seconde pompe (42) qui alimente un circuit de refroidissement dans le cadre d'un fonctionnement en circuit fermé presque sans puissance. Lorsque la pression de l'accumulateur chute en-dessous d'une valeur seuil pSU, un dispositif de charge d'accumulateur (41, 42, 59) permet de pouvoir recharger l'accumulateur à une pression pS, qui est nettement supérieure à la pression de fonctionnement pB. La première pompe (41) est conçue pour un débit qui couvre le flux d'huile de fuite lors du fonctionnement normal et qui maintient la pression de l'accumulateur à une valeur minimale pS à laquelle la pression de fonctionnement pB est stable. Le dispositif de charge d'accumulateur comprend une soupape de commutation (59) qui fait également passer la seconde pompe (42) en fonctionnement de charge de l'accumulateur lorsque la pression de l'accumulateur chute en-dessous de la valeur seuil inférieure de commutation pSU. La seconde pompe revient en fonctionnement en circuit fermé lorsque l'accumulateur (52) est de nouveau chargé à une valeur seuil de commutation pSO nettement supérieure.
PCT/EP2002/000275 2001-01-12 2002-01-14 Dispositif d'alimentation en huile sous pression destine a un consommateur hydraulique fonctionnant avec une pression de fonctionnement pb definie WO2002055886A2 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
DE50209473T DE50209473D1 (de) 2001-01-12 2002-01-14 Einrichtung zur druckölversorgung eines mit einem definierten betriebsdruck betriebenen hydraulischen verbrauchers
EP02706702A EP1350033B1 (fr) 2001-01-12 2002-01-14 Dispositif d'alimentation en huile sous pression destine a un consommateur hydraulique fonctionnant avec une pression de fonctionnement definie

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10101481 2001-01-12
DE10101481.3 2001-01-12

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WO2002055886A2 true WO2002055886A2 (fr) 2002-07-18
WO2002055886A3 WO2002055886A3 (fr) 2003-01-09

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

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CN107504015A (zh) * 2017-10-10 2017-12-22 宁波创力液压机械制造有限公司 一种电缆拉力测试装置
CN113931728A (zh) * 2021-01-19 2022-01-14 吉利汽车研究院（宁波）有限公司 一种油蒸气的控制方法、装置、系统和存储介质
US11506231B2 (en) * 2018-10-08 2022-11-22 Saab Ab Multirod fluid actuator arrangement

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CN106122130B (zh) * 2016-07-08 2018-09-28 江苏元利数控机床有限公司 压力可控的夹具液压装置的控制方法

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN107504015A (zh) * 2017-10-10 2017-12-22 宁波创力液压机械制造有限公司 一种电缆拉力测试装置
CN107504015B (zh) * 2017-10-10 2024-04-05 宁波创力液压机械制造有限公司 一种电缆拉力测试装置
US11506231B2 (en) * 2018-10-08 2022-11-22 Saab Ab Multirod fluid actuator arrangement
CN113931728A (zh) * 2021-01-19 2022-01-14 吉利汽车研究院（宁波）有限公司 一种油蒸气的控制方法、装置、系统和存储介质
CN113931728B (zh) * 2021-01-19 2023-03-28 吉利汽车研究院（宁波）有限公司 一种油蒸气的控制方法、装置、系统和存储介质

Also Published As

Publication number Publication date
EP1350033A2 (fr) 2003-10-08
DE50209473D1 (de) 2007-03-29
EP1350033B1 (fr) 2007-02-14
WO2002055886A3 (fr) 2003-01-09
ATE354030T1 (de) 2007-03-15
DE10201183A1 (de) 2002-08-14

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