EP1350033B1 - Dispositif d'alimentation en huile sous pression destine a un consommateur hydraulique fonctionnant avec une pression de fonctionnement definie - Google Patents

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

Info

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
Authority
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
Other languages
German (de)
English (en)
Other versions
EP1350033A2 (fr
Inventor
Dieter Jordan
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Voith Turbo H and L Hydraulic GmbH and Co KG
Original Assignee
Voith Turbo H and L Hydraulic GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Family has litigation
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=EP1350033(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Voith Turbo H and L Hydraulic GmbH and Co KG filed Critical Voith Turbo H and L Hydraulic GmbH and Co KG
Publication of EP1350033A2 publication Critical patent/EP1350033A2/fr
Application granted granted Critical
Publication of EP1350033B1 publication Critical patent/EP1350033B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

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.

Landscapes

  • 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)

Claims (11)

  1. Dispositif d'alimentation en huile sous pression destiné à un consommateur hydraulique (11) dans le fonctionnement duquel un courant d'huile de fuite significatif se produit, ainsi que d'alimentation en huile sous pression intermittente destiné à au moins un autre consommateur hydraulique (61), avec un groupe d'alimentation de pression (33) qui comprend une première pompe fonctionnant de manière permanente au sens d'une charge d'un accumulateur de pression (52) du dispositif d'alimentation en huile sous pression utilisé comme source de pression pour les consommateurs (11, 61), ainsi qu'une deuxième pompe (42) fonctionnant de manière permanente, et avec un dispositif de charge d'accumulateur (41, 42, 49) commandé par un dispositif de surveillance de pression (59, 64) du dispositif d'alimentation en huile sous pression, au moyen duquel l'accumulateur de pression (52) peut être chargé à une pression ps qui est significativement plus élevée que la pression de fonctionnement pB utilisée dans le consommateur, dans lequel
    a) la première pompe (41) est conçue pour un débit qui est suffisant pour couvrir un montant prédéterminé du courant d'huile de fuite lié au fonctionnement d'un consommateur hydraulique (11) et maintenir la pression de l'accumulateur à l'intérieur d'une plage de variation admissible à une valeur ps à laquelle est liée une stabilité suffisante d'une pression de service pB définie dont le consommateur (11) a besoin,
    caractérisé en ce que
    b) la deuxième pompe (42) alimente un circuit de refroidissement du dispositif d'alimentation en huile sous pression dans lequel de l'huile hydraulique s'écoule à partir d'un réservoir de stockage (32) du groupe d'alimentation de pression et retourne au réservoir de stockage en passant par un refroidisseur d'huile (57) dans un fonctionnement de circulation de la pompe (42) pratiquement sans débit, en ce que
    c) le dispositif de charge de l'accumulateur comprend une vanne de commutation commandée par pression (59 ; 59/1, 59/2) qui, en cas de baisse de la pression de l'accumulateur au-dessous d'une valeur de seuil de commutation inférieure psu, fait passer la deuxième pompe (42) à un fonctionnement de charge dans lequel cette pompe également permet la charge de l'accumulateur de pression (52) ainsi que l'alimentation sous pression du consommateur (11) et, après que l'accumulateur de pression a été chargé de nouveau à une valeur de seuil de commutation significativement plus élevée pso, la deuxième pompe est commutée à nouveau sur le fonctionnement de circulation, en ce que
    d) les deux pompes (41) et (42) sont réalisées sous la forme de pompes à cylindrée constante et en ce que
    e) la deuxième pompe (42) est conçue pour un débit significativement plus élevé que la première pompe.
  2. Dispositif selon la revendication 1, caractérisé en ce que la deuxième pompe (42) présente un débit situé entre le double et le triple du débit de la première pompe (41).
  3. Dispositif selon la revendication 1 ou la revendication 2, caractérisé en ce que la vanne de commutation (59) est réalisée sous la forme d'une vanne commandée par pression dont la valeur de seuil de commutation inférieure Psu au-dessous de laquelle elle provoque la commutation de la deuxième pompe (42) du fonctionnement de circulation au fonctionnement de charge est inférieure de 5 à 20% à la pression de sortie maximale du groupe d'alimentation de pression (33) qui est prédéterminée par le réglage d'une soupape de limitation de pression (49) du groupe d'alimentation de pression (33) et dont la valeur de seuil de commutation supérieure pso au-dessus de laquelle la vanne de commutation (59) fait passer à nouveau la deuxième pompe (42) à son fonctionnement de circulation est inférieure de 1 à 3% à la pression de sortie maximale du groupe d'alimentation de pression (33).
  4. Dispositif selon l'une des revendications 1 à 3, caractérisé en ce qu'au moins la première pompe (41) peut être commandée selon le signal de sortie d'un capteur de pression (64) électronique ou électromagnétique du dispositif d'alimentation en huile sous pression, de telle manière que le débit de la première pompe (41) augmente de manière compensatoire avec la baisse de la pression dans le circuit de consommateur .
  5. Dispositif selon la revendication 4, caractérisé en ce que le débit de la deuxième pompe (42) varie également dans le même sens avec une variation du débit de la première pompe (41).
  6. Dispositif selon la revendication 5, caractérisé en ce que les deux pompes (41 et 42) sont réalisées sous la forme de pompes à cylindrée constante qui sont entraînées à vitesse gouvernable ou réglable par un moteur électrique commun (48) du groupe d'alimentation de pression (33).
  7. Dispositif selon l'une des revendications 4 à 6, caractérisé en ce qu'il est prévu un capteur de température électronique ou électromécanique (67), qui produit un signal de sortie électrique caractéristique de préférence de la température de l'huile hydraulique dans le réservoir de stockage, et une unité de commande (66) électronique qui répond à ce signal de sortie et commande une augmentation du débit d'au moins la première pompe (41) dans une relation monotone avec une augmentation de la température de l'huile.
  8. Dispositif selon l'une des revendications 1 à 7, utilisable pour l'alimentation en huile sous pression d'un cylindre de serrage hydraulique (11) avec lequel peut être actionné un dispositif de serrage (12) au moyen duquel une pièce peut être fixée de manière résistant à la rotation sur une tige de travail (16) pouvant être entraînée en rotation d'une machine-outil, dans lequel
    a) le piston du cylindre de serrage est relié de manière résistant à la rotation à la tige de travail (16) et l'accouplement de pression a lieu dans un espace de pression (19 ou 21) du cylindre de serrage (11) utilisé pour serrer - serrage extérieur ou serrage intérieur - le dispositif de serrage (12) par l'intermédiaire d'un passage tournant hydraulique (34), en outre
    b) il est prévu une vanne de prédétermination de pression de serrage (38) qui est réalisée sous la forme d'une soupape de limitation de pression à pression de sortie pB réglable pour prédéterminer la pression de fonctionnement pB dont le cylindre de serrage (11) a besoin et
    c) entre la vanne de prédétermination de pression de serrage (38) et le cylindre de serrage (11) est montée une soupape de commande de fonction (22) pouvant être commandée de préférence électriquement avec des positions de fonction à crans (I et II) qui sont associées aux états de fonctionnement de serrage alternatifs - serrage extérieur et serrage intérieur - du cylindre de serrage (11) ou du dispositif de serrage (12).
  9. Dispositif selon la revendication 8, caractérisé en ce qu'il est prévu une unité de commande électronique, qui règle automatiquement le débit d'au moins la première pompe (41) et de préférence des deux pompes (41 et 42) en fonction de la température de fonctionnement, de la vitesse de rotation de la tige et de la force de serrage du cylindre de serrage, de préférence dans le sens d'une superposition linéaire des valeurs de réglage associées à ces paramètres.
  10. Dispositif selon l'une des revendications 1 à 9, caractérisé en ce que le refroidisseur d'huile (57) comprend un ventilateur de refroidissement (71) avec débit d'air de refroidissement pouvant être commandé.
  11. Dispositif selon l'une des revendications 1 à 10, caractérisé en ce que la sortie (72) d'une soupape de limitation de pression (49) prévue pour prédéterminer une pression de sortie maximale du groupe d'alimentation de pression (33) est raccordée à un chemin de courant de circulation (58) qui relie la vanne de commutation (59) au refroidisseur d'huile (27).
EP02706702A 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 Expired - Lifetime EP1350033B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10101481 2001-01-12
DE10101481 2001-01-12
PCT/EP2002/000275 WO2002055886A2 (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 pb definie

Publications (2)

Publication Number Publication Date
EP1350033A2 EP1350033A2 (fr) 2003-10-08
EP1350033B1 true EP1350033B1 (fr) 2007-02-14

Family

ID=7670551

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02706702A Expired - Lifetime 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

Country Status (4)

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

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2022990B1 (fr) 2007-08-07 2016-10-12 HAWE Hydraulik SE Machine outil et unité d'alimentation
DE102012002224A1 (de) * 2012-02-04 2013-08-08 Hydac Cooling Gmbh Ventil
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
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
WO2020076199A1 (fr) * 2018-10-08 2020-04-16 Saab Ab Agencement d'actionneur fluidique à tiges multiples
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

Family Cites Families (5)

* Cited by examiner, † Cited by third party
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 (de) * 1983-05-12 1984-10-31 Orsta Hydraulik Veb K Leistungsgeregelte druckspeichersysteme fuer hydraulische antriebe
DE19925665B4 (de) * 1999-06-04 2005-03-24 Zf Sachs Ag Verfahren zum Einstellen des Systemdrucks in einem hydraulischen Stellantrieb und hydraulischer Stellantrieb

Also Published As

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

Similar Documents

Publication Publication Date Title
DE3629638C2 (de) Kolbenpumpe mit variierbarer Verdrängung
EP1100670A1 (fr) Systeme d'entrainement hydrostatique pour presse d'injection et son procede de fonctionnement
WO1997014889A1 (fr) Regulation de puissance avec detection de charge
EP3077674B1 (fr) Système hydraulique
EP2488764A1 (fr) Agencement de soupape
EP1989450B1 (fr) Dispositif de commande hydraulique
AT516316A2 (de) Hydraulische Schaltung und Maschine mit einer hydraulischen Schaltung
WO1998010889A1 (fr) Dispositif a broche porte-piece pour une machine-outil
DE3516747C2 (de) Steuereinrichtung für ein hydrostatisches Getriebe
EP1350033B1 (fr) Dispositif d'alimentation en huile sous pression destine a un consommateur hydraulique fonctionnant avec une pression de fonctionnement definie
EP3584450B1 (fr) Engin de travail utilisable dans l'agriculture ou les travaux publics avec une commande de signal de charge d'une section hydraulique de travail d'un appareil auxiliaire
CH700344B1 (de) Steuervorrichtung für mindestens zwei hydraulische Antriebe.
EP0423257B1 (fr) Dispositif pour pompes hydrostatiques a refoulement variable
EP1766246B1 (fr) Procede de commande d'un systeme a vannes pour dispositif de levage
WO2018108615A1 (fr) Entraînement hydraulique à course rapide et course en charge
EP0884476B1 (fr) Circuit de contrôle de pression de sécurité pour une pompe hydraulique radiale ou axiale à cylindrée variable ou une machine à cellules semi-rotatives
EP3135924B1 (fr) Commande hydraulique
EP2022990B1 (fr) Machine outil et unité d'alimentation
EP1253327B1 (fr) Circuit de commande hydraulique
DE4337210A1 (de) Zentralhydraulikanlage für ein Kraftfahrzeug
EP1136702B1 (fr) Alimentation d'eau à pression
EP0884484A1 (fr) Dispositif de serrage électrohydraulique
DE102021121843B3 (de) Hydropneumatisches Federungssystem
DE102010017208B4 (de) Kühlmittelsystem für Werkzeugmaschinen
DE102018212854B4 (de) Hochdruckschutzsystem

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20030708

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

AX Request for extension of the european patent

Extension state: AL LT LV MK RO SI

17Q First examination report despatched

Effective date: 20041220

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RTI1 Title (correction)

Free format text: DEVICE FOR THE FORCE OIL FEED OF A HYDRAULIC CONSUMER OPERATED AT A DEFINED OPERATING PRESSURE

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: VOITH TURBO H + L HYDRAULIC GMBH & CO. KG

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE CH CY DE DK ES FI FR GB GR IE IT LI LU MC NL PT SE TR

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070214

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070214

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070214

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070214

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REF Corresponds to:

Ref document number: 50209473

Country of ref document: DE

Date of ref document: 20070329

Kind code of ref document: P

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070514

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20070425

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070525

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070716

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

26 Opposition filed

Opponent name: HAWE HYDRAULIK GMBH & CO. KG

Effective date: 20070814

EN Fr: translation not filed
PLAX Notice of opposition and request to file observation + time limit sent

Free format text: ORIGINAL CODE: EPIDOSNOBS2

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070515

Ref country code: FR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20071005

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20080118

Year of fee payment: 7

PLBB Reply of patent proprietor to notice(s) of opposition received

Free format text: ORIGINAL CODE: EPIDOSNOBS3

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: AT

Payment date: 20080110

Year of fee payment: 7

BERE Be: lapsed

Owner name: VOITH TURBO H + L HYDRAULIC G.M.B.H. & CO. KG

Effective date: 20080131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070214

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070214

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090131

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090131

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20090114

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20080114

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20070214

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20110127

Year of fee payment: 10

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20110120

Year of fee payment: 10

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20120114

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120114

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20120114

PLCK Communication despatched that opposition was rejected

Free format text: ORIGINAL CODE: EPIDOSNREJ1

PLBN Opposition rejected

Free format text: ORIGINAL CODE: 0009273

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: OPPOSITION REJECTED

27O Opposition rejected

Effective date: 20130611

REG Reference to a national code

Ref country code: DE

Ref legal event code: R100

Ref document number: 50209473

Country of ref document: DE

Effective date: 20130611

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20200121

Year of fee payment: 19

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50209473

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20210803