EP0584078B1 - Dispositif de protection contre les surcharges pour un moteur d'entrainement d'une pompe principale d'une unite hydraulique d'alimentation en pression - Google Patents

Dispositif de protection contre les surcharges pour un moteur d'entrainement d'une pompe principale d'une unite hydraulique d'alimentation en pression Download PDF

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Publication number
EP0584078B1
EP0584078B1 EP92905344A EP92905344A EP0584078B1 EP 0584078 B1 EP0584078 B1 EP 0584078B1 EP 92905344 A EP92905344 A EP 92905344A EP 92905344 A EP92905344 A EP 92905344A EP 0584078 B1 EP0584078 B1 EP 0584078B1
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EP
European Patent Office
Prior art keywords
pressure
valve
control chamber
main
consumer
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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
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EP92905344A
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German (de)
English (en)
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EP0584078A1 (fr
Inventor
Hartmut Benckert
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Putzmeister Concrete Pumps GmbH
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Putzmeister Werk Maschinenfabrik GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—Hydraulic systems to change the pump delivery
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/10—Other safety measures
    • F04B49/103—Responsive to speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B3/00—Engines characterised by air compression and subsequent fuel addition
    • F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition

Definitions

  • a hydraulically driven thick matter feed pump e.g. a two-cylinder pump for concrete
  • the delivery cylinders of which are driven by means of a hydraulic drive cylinder, by means of which alternating pressurization with the outlet pressure of a pressure supply unit and relief thereof to the tank of the pressure supply unit are intended to achieve continuous concrete delivery, in the event of drastic load fluctuations In the area of the thick matter pump malfunctions a stalling to drive a eg
  • constant volume flow controlled main pump of the pressure supply unit it is known to electronically record the speed of the diesel engine and, if it drops below a threshold value considered critical, the flow rate actuator of the main pump of the pressure supply unit via an electro-hydraulic control device To control the reduction of the volume flow generated by the main pump in order to reduce its torque requirement to such an extent that it can still be covered by the drive motor and the same can be prevented from stalling.
  • the control pressure is generated by means of a pressure adder from the load-dependent pressure in the main line and the constant base pressure tapped before a pressure limiting valve connected downstream of the tapping point of the secondary circuit, whereby a reduction in the pump output is to be achieved when an overload occurs at a low engine speed, while otherwise
  • the delivery rate is also maximized in the underspeed range of the engine.
  • the main disadvantage is that a pressure-variable consumer cannot be switched on in the secondary circuit and that necessary auxiliary functions must therefore be performed by additional units.
  • DE-OS 23 63 480 per se to provide a hydraulic adjusting device for a pump for generating a constant flow rate, the adjusting member of which is regulated with the aid of two adjusting pistons which can be acted upon by a differential pressure derived from the main consumer circuit in such a way that the output volume flow of the pump is reduced with increasing differential pressure and increased with decreasing differential pressure.
  • a three-way flow control valve arranged in the main circuit is provided, which has a connection to a tank via two series-connected throttles, one of the pistons being acted upon by a residual flow branched off between the throttles, while the other is optionally supplied by one Auxiliary pump generated delivery pressure is applied.
  • a protective circuit against overloading the pump drive is not provided.
  • the protective device designed as a purely hydraulic device and using hydraulic regulators and actuators of the main pump, which are already available for their volume flow control, works very reliably and is - thanks to the multiple use of existing hydraulic functional elements - compared to a pressure supply unit without such a protective device Can be realized with comparatively little additional technical effort, which is essentially due to the additional auxiliary pump, a simple pressure-controlled changeover valve and simple flow resistance elements, an effort which, however, is not significant if these functional elements of the protective device are part of the entire pump device, as provided in accordance with claim 2, can be used to fulfill further functions that are necessary anyway and require a secondary consumer group.
  • the consumer fed in the secondary consumer circuit is connected directly to the high-pressure outlet of the auxiliary pump and one for sensing that generated by the auxiliary pump Adjusted flow throttle provided between the consumer and the tank of the pressure supply unit, a simple control valve designed for a low control pressure level is sufficient to control the protective function.
  • the adjustable flow resistance provided for sensing the volume flow generated by the auxiliary pump is connected directly to the pressure output of the auxiliary pump and the e.g. flow resistance formed by a further consumer between the adjusting throttle and the tank of the pressure supply unit, a valve designed for a high control pressure level is required as a protective function control valve, but this can be integrated into the auxiliary pump, which is important both in terms of design and in terms of sensitivity the control is advantageous.
  • control valve according to claim 6 for example as a proportional valve, optionally with the functional positions indicated by the features of claim 7, the response characteristic of the actuating device can be influenced in a simple manner, by means of which the delivery volume of the main pump can be adjusted and thus also a desired application. and discharge characteristics of the pressure supply unit can be achieved overall.
  • control valve provided in accordance with claim 8 can be expedient in order to avoid "oscillation" of the volume flow control in the low speed range of the drive motor.
  • the features of claim 9 indicate a relationship of the flow resistances of the consumer which is favorable from the point of view of a good use of energy and an adjustment throttle of the secondary consumer circuit.
  • the main pump 12 is provided as a swash plate axial piston pump, which can be infinitely adjusted with respect to its delivery volume by swiveling its swash plate represented by the double arrow 14, which values can be changed between a minimum value Q min and a maximum value Q max .
  • the position of the swash plate 14 corresponding to the minimum delivery volume, shown in broken lines, is the one in which its normal runs parallel to the axes of the axial piston pump elements (not shown). In the position of the swash plate 14 corresponding to the maximum delivery volume Q max , its normal runs, for example, at an angle of 30 ° to the central axes of the axial piston pump elements.
  • a throttle 18 with an adjustable flow resistance is connected as a load sensor element, via which a pressure drop ⁇ P occurs during operation of the pressure supply unit 10 and the consumer 11, by which the pressure at the center tap 19 - between the throttle 18 and the high-pressure supply connection 17 of the consumer 11 - the effective supply pressure P V that can be tapped is lower than the outlet pressure P H of the main pump 12 at its high-pressure outlet 16.
  • two linear cylinders 21 and 22 are provided, by means of which oppositely directed torques can be exerted on the swivel plate 14, from their respective equilibrium the respective swivel position of the swivel plate 14 and the associated delivery rate of the main pump 12 result.
  • the drive pressure chamber 29 of the second linear cylinder 22, by means of the pressurization of which a moment urging the control disk 14 in its pivot position associated with its minimum delivery volume can be generated, can alternatively be connected to the - pressure-less - tank 32 of the pressure supply unit 10 or to the pressure-less control valve 31 acting as a pressure compensator High pressure outlet 16 of the main pump 12 can be connected.
  • the prestressed compression spring 28 of the first linear cylinder 21 also acts as a return spring for the second linear cylinder 22, the piston 33 thereof urges into the basic position associated with the minimal volume of its drive pressure chamber 29.
  • the control valve 31 is designed as a 3/2-way valve, which is forced into its illustrated basic position 0 by a valve spring 34, in which the drive pressure chamber 29 of the second linear cylinder 22 is connected to the unpressurized tank 32 of the pressure supply unit and against the high-pressure outlet 16 Main pump 12 is shut off.
  • a first control chamber 36 of the control valve 31 with the high output pressure P H of the main pump 12, the control valve 31 can be controlled into its function position I, which is alternative to the basic position zero, in which the drive pressure chamber 29 of the second linear cylinder is connected to the high pressure output 16 of the main pump 12 and now is blocked against the unpressurized tank 32 of the pressure supply unit 10.
  • control valve 31 By acting on a second control chamber 37 of the control valve 31 with the on the center tap 19 between the Throttle 18 and the consumer 11 pending, compared to the high output pressure P H of the main pump 12 pressure P V , the control valve 31 is pushed into its zero basic position.
  • the control valve 31 is designed as a proportional valve, in which an increasing deflection of its valve piston represented by the switching symbol 38 from its spring-centered end position as the basic position zero initially has a decrease in the flow cross section of the flow path 39 connecting the drive pressure chamber 29 of the second linear cylinder to the tank 32 until this occurs is blocked and a further deflection of the valve piston 38, which leads to the taking of the functional position I, to an increasing, ie cross-section-increasing release of the flow path 41, via which the drive pressure chamber 29 of the second linear cylinder 22 is connected to the high-pressure outlet 16 of the main pump 12 in the functional position I.
  • the pressure supply unit 10 operates when and as long as the center tap 19 between the throttle 18 and the consumer 11 is connected to the second control chamber 37 of the control valve 31, as follows: Before switching on the diesel engine 13 and thus activating the pressure supply unit 10 and starting up the consumer 11, which is connected between the adjustable throttle 18 and the tank 32 of the pressure supply unit 10, the two linear cylinders 21 and 22 are in their illustrated, with maximum delivery volume the main pump 12 linked basic positions, and the piston 38 of the control valve 31 assumes its spring-centered end position linked to the maximum flow cross section of the flow path 39 effective in the basic position 0 of the control valve 31.
  • preliminary activation of the main pump 12 increases to the extent that the flow rate of the oil flow conveyed by the main pump 12 through the throttle 18 and the consumer 11 increases, the pressure P H at the high pressure output of the Main pump and also on the center tap 19 between the throttle 11, the pressure difference ⁇ P - the pressure drop across the throttle 18 - between the high pressure outlet 16 of the main pump 12 and the center tap 19 or the high pressure supply connection 17 of the consumer 11 also according to the amount grows.
  • the difference ⁇ F by which the effective cross-sectional area F2 of the piston 33 of the second linear cylinder 22 is larger than the effective cross-sectional area F1 of the first linear cylinder 21, is dimensioned such that even at relatively low output pressures of the main pump 12 of, for example, 6 to 12 bar, the force deployed by the second linear cylinder 22 is sufficient to to "overpress" the first linear cylinder 21 and to achieve a rotation of the swivel plate 14 into its position linked to the minimum delivery volume of the main pump 12.
  • the control valve 31, the linear cylinders 21 and 22 acting on the swivel plate 14 of the main pump 12 and the throttle 18 connected between the main pump 12 and the consumer 11 provide stabilization of the oil flow flowing via the throttle 18 and the consumer 11 to the tank 32 of the pressure supply unit 10 to an amount which can be predetermined indirectly through the adjustable preload of the valve spring 34 of the control valve 31. It is therefore irrelevant within a wide setting range of the throttle 18 to what amount of its flow resistance the throttle 18 is set.
  • a protective device designated overall by 40 provided that, in cases in which the output torque of the diesel engine 13 is no longer sufficient to drive the main pump 12 in the sense of maintaining a predetermined output volume flow, reliably precludes the diesel engine 13 from stalling, which could lead to considerable malfunctions.
  • a related need situation can arise from a malfunction of the consumer 11, but can also occur in a controlled manner, e.g. characterized in that the throttle 18 is automatically set to increased flow resistance in the final phases of such strokes to achieve a gentle reversal of piston movements of the consumer 11.
  • the protective device 40 comprises an auxiliary pump 42 which, like the main pump 12, is driven by the diesel engine 13 and one which is proportional to the speed of the diesel engine 13 Volume flow generated.
  • auxiliary pump 42 which, like the main pump 12, is driven by the diesel engine 13 and one which is proportional to the speed of the diesel engine 13 Volume flow generated.
  • a hydraulic series circuit consisting of a consumer 44 represented by a fixed throttle and an adjusting throttle 46, via which the outlet pressure P A of the auxiliary pump 42 drops, the one above the components of this series circuit - the consumer 44 and the adjusting throttle 46 - occurring pressure drops .DELTA.P V and .DELTA.P D are proportional to the flow resistances of the consumer 44 and the adjusting throttle 46 and, in total, give the value of the outlet pressure P A of the auxiliary pump 42.
  • the protective device 40 comprises a 3/2-way valve Control valve, which is designed as a pressure-controlled valve, which is urged into its basic position 0 by a prestressed valve spring 48, in which the second control chamber 37 of the pressure-controlled control valve 31 of the pressure supply unit 10 is connected to the tank 32 of the pressure supply unit 10 and this control chamber 37 against the Center tap 19 between the throttle 18 and the consumer 11 is shut off, and this by pressurizing a control chamber 49 with the pressure prevailing between the consumer 44, which is connected to the auxiliary pump 42 and the adjusting throttle 46, the amount of the pressure drop ⁇ P D across the adjusting throttle 46 corresponds to in ne functional position I can be controlled, in which the one used on the center tap 19 between the load sensor element Setting throttle 18 and the pressure prevailing in the consumer 11 is coupled into the second control chamber 37 of the control valve 31 and this control chamber 37 is blocked off
  • the protective device explained so far works as follows: As long as the speed of the diesel engine 13 is higher than a predeterminable threshold value above which a stalling of the diesel engine 13 can be excluded with sufficient certainty, the pressure drop across the adjusting throttle 46 of the protective device 40 and thus the pressure coupled into the control chamber 49 of the control valve 47 is sufficient large to hold the control valve 47 against the action of its valve spring 48 in its functional position I, in which the pressure at the center tap 19 of the main pump circuit is coupled into the second control chamber 37 of the control valve 31 and the pressure supply unit 10 in the normal, load-sensing Control mode works.
  • the speed threshold below which the control valve 47 changes from its functional position I assigned to normal control operation to its basic position 0, which provides protection of the diesel engine 13 against stalling, can be predetermined by setting a specific flow resistance of the adjusting throttle 46.
  • the control pressure from which the control valve 47 is switched to its functional position I is between 4 and 10 bar.
  • the protective device 50 shown in FIG. 2 is functionally equivalent to the protective device 40 according to FIG. 1, but differs from this in terms of circuit technology in that the setting throttle 46, by means of which the speed threshold can be specified as a result, below which the second control chamber 37 of the control valve 31 is depressurized, connected directly to the high-pressure outlet 43 of the auxiliary pump 42 and the consumer 44 is connected between this adjusting throttle 46 and the tank 32 of the pressure supply unit, and in that the control valve 47 ', which is in its basic position 0 and in it Alternative function position I conveys the same functions as the control valve 47 of the protective device 40 according to FIG.
  • a differential valve which is switched from its basic position 0 to its function position I when the pressure difference ⁇ P D between the high-pressure outlet 43 of the auxiliary pump 42 and de r center tap 51 between the adjusting throttle 46 and the consumer 44 exceeds a threshold value, the amount of which can be the same as the control pressure that builds up in the exemplary embodiment according to FIG. 1 via the adjusting throttle 46 connected there between the consumer 44 and the tank 32.
  • control valve 47 'of the protective device 50 according to FIG. 2 in addition to the first control chamber 49', which is acted upon by the output pressure present at the high-pressure outlet 43 of the auxiliary pump 42, whereby the control valve 47 'is forced into its functional position I.
  • control valve 47 ' is acted upon by the pressure present at the center tap 51 between the setting throttle 46 and the consumer 44, whereby the control valve 47 'is pushed into its basic position 0, these control chambers 49' and 52 'being designed such that the forces resulting from their pressurization acting in the opposite direction on the valve piston cancel each other out, so that in the control valve 47 'the pressurization of its second control chamber 52 determines the pressure level against which the pressure coupled into the first control chamber 49' must be higher , so that the control valve 47 'against the action its valve spring 48 can be switched to its functional position I.
  • the control valve 47 ' is also designed so that this pressure difference is only a few bar, e.g. 6 bar.
  • the control chambers 49 'and 52 of the control valve 47' are acted upon by the absolute amount after significantly higher pressures than the control chamber 49 of the control valve 47 Protective device 40 according to FIG. 1, which places increased demands on the tightness of the control chambers 49 and 52.
  • the protective device 50 according to FIG. 2 it is readily possible to structurally combine the control valve 47 'and the adjusting throttle 46 with the auxiliary pump 42 in an integrated construction, since the consumer 44 is hydraulically connected downstream of this hydraulic functional unit.
  • control valve 47 or 47 ' can be designed as a proportional valve, which increases after a transition from one to the other of the possible functional positions 0 and I Opening cross sections of the effective circulation or flow flow paths 53 and 54 releases, whereby particularly gentle and therefore gentle starting and stopping characteristics of the main pump 12 can be achieved in switching situations of the consumer 11 of the main circuit.
  • control valve 47 or 47 ' this is, as not specifically shown, designed as a 3/3-way valve, which between the functional position 0, in which the second control chamber 37 of the control valve 31 against the reference pressure tap 19 of the main consumer circuit 11, 18, but is connected to the tank 32 of the pressure supply unit 10, and the functional position I, in which the second control chamber 37 of the control valve 31 is connected to the comparative pressure tap 19 of the main consumer circuit, but against the tank of the pressure supply unit 10 is locked, a locking position II has, in which the second control chamber 37 of the control valve 31 is shut off both against the reference pressure tap 19 of the main consumer circuit 11, 18 and against the tank 32 of the pressure supply unit 10.
  • the changeover positions in which the control valve changes from its blocking functional position II into its one flow position 0 or the alternative flow position I, seen in the direction of displacement of the valve body can be arranged at a distance from one another , which is between 1/50 and 1/5, preferably around 1/10 of the total stroke that the valve body can carry out between its end positions assigned to the alternative flow function positions 0 and I, respectively.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Control Of Vehicle Engines Or Engines For Specific Uses (AREA)

Abstract

Sur une unité hydraulique d'alimentation en pression comportant une pompe principale entraînée par un moteur diesel, un circuit utilisateur principal raccordé à cette pompe est formé d'une bobine de réglage (18) raccordée directement à la pompe principale et d'un récepteur (11) branché en série avec cette bobine. A partir d'une comparaison de la pression de sortie PH couplée dans une première chambre de commande d'une vanne de réglage (31) avec la pression de référence PV mesurable entre la bobine (18) et le récepteur principal (11) et pouvant être couplée dans une deuxième chambre de réglage (37) de la vanne de réglage (31), cette dernière provoque une commande d'un dispositif de réglage (21, 22) de telle manière que le débit volumique dans le circuit récepteur prinpipal (16, 11) reste constant. Un dispositif de protection destiné à empêcher un étouffement du moteur diesel (13) dans des situations de charge exceptionnelles comprend une pompe auxiliaire (42) entraînée par ce moteur diesel, pompe qui produit un débit volumique à la sortie proportionnel au nombre de tours, lequel traverse une autre bobine de réglage (46) et un récepteur (44) disposé après cette bobine et en synchronisme avec la vitesse de rotation, ainsi qu'une vanne (47) commandée par la pression, par l'intermédiaire de laquelle la deuxième chambre de commande (37) de la soupape de réglage (31) se détend en direction du réservoir (32), ce qui a pour effet de régler la pompe principale (12) sur des volumes déplacés minimums lorsque le nombre de tours du moteur est abaissé au-dessous d'un seuil déterminé.

Claims (9)

  1. Dispositif de protection contre les surcharges pour un moteur d'entraînement (13) conformé en moteur à combustion interne et notamment en moteur Diesel et destiné à une pompe principale (12) d'un groupe d'alimentation en pression hydraulique (10) qui, au moyen d'un dispositif de réglage hydraulique prévu pour stabiliser le courant volumique circulant dans un circuit d'utilisation principal qui est raccordé à la sortie haute pression (16) de la pompe principale (12), conduisant au réservoir (32) du groupe d'alimentation en pression (10) et fermé par l'intermédiaire de la pompe (12), peut être réglée par un courant de fluide sous pression pour la surveillance duquel est prévu un étranglement (18) monté en série avec l'utilisateur principal (11) et provoquant une chute de pression (ΔP) caractéristique pour la valeur effective du courant volumique passant par l'utilisateur principal (11), dont la détection au moyen d'une vanne-pilote (31) qui, à partir d'une comparaison de la pression de sortie PH de la pompe principale (12) établie comme pression de référence dans une première chambre de commande (36) de ladite vanne-pilote, avec la pression PV régnant à la prise (19) entre l'étranglement (18) et l'utilisateur principal (11) et envoyée comme pression de comparaison dans une seconde chambre de commande (37) de la vanne-pilote (31), règle une pression de commande établie dans un dispositif de réglage hydraulique (22) de la pompe principale (12) de telle façon que le courant volumique de sortie de la pompe principale (12) est réduit avec l'augmentation de la pression différentielle (ΔP) sur l'étranglement (18) et que le courant volumique est augmenté au fur et à mesure que la pression différentielle (ΔP) diminue, caractérisé en ce qu'il comprend une pompe auxiliaire (42) entraînée, elle aussi, à vitesse de rotation synchrone, au moyen du moteur d'entraînement (13) de la pompe principale (12), et produisant un courant volumique de sortie proportionnel à la vitesse de rotation qui, par l'intermédiaire d'un circuit d'utilisation secondaire comprenant hydrauliquement un montage en série d'une résistance hydraulique (46) réglable et d'une résistance hydraulique supplémentaire (44) et pourvu d'une prise à laquelle la pression varie avec le courant volumique, est amené au réservoir (32) du groupe d'alimentation en pression (10), et qu'il est prévu, pour l'alimentation de la seconde chambre de commande (37) de la vanne-pilote (31) avec la pression de comparaison (PV) disponible à la prise (19) du circuit d'utilisation principal (11, 18), une vanne (47, 47') commandée par pression qui peut être poussée, par un ressort de soupape (48) précontraint, dans une position de base (0) dans laquelle la seconde chambre de commande (37) de la vanne-pilote (31) est déchargée, et amenée, par l'alimentation d'une chambre de commande (49, 49') avec la pression régnant à la prise du circuit d'utilisation secondaire (44, 46), dans une position de fonctionnement (I) dans laquelle la pression de comparaison (PV) apparaissant dans le circuit d'utilisation principal (11, 18) est appliquée à la seconde chambre de commande (37) de la vanne-pilote (31).
  2. Dispositif de protection selon la revendication 1, caractérisé en ce que la résistance hydraulique supplémentaire (44) du circuit d'utilisation secondaire (46, 44) est réalisée sous la forme d'un utilisateur à vitesse de rotation synchrone, par exemple d'un agitateur à entraînement hydraulique.
  3. Dispositif de protection selon l'une des revendications 1 ou 2, caractérisé en ce que la résistance hydraulique (44) du circuit d'utilisation secondaire est raccordée directement à la sortie de pression (43) de la pompe auxiliaire (42), et que la résistance hydraulique (46) - réglable - prévue pour la détection du courant volumique est intercalée entre la résistance hydraulique (44) et le réservoir (32) du groupe d'alimentation en pression (10).
  4. Dispositif de protection selon l'une des revendications 1 ou 2, caractérisé en ce que la résistance hydraulique réglable (46) du circuit d'utilisation secondaire (46, 44) est raccordée directement à la sortie de pression (43) de la pompe auxiliaire (42), et que la résistance hydraulique (44) ou l'utilisateur (44) du circuit d'utilisation secondaire (46, 44) est intercalé entre la résistance hydraulique réglable (46) et le réservoir (32) du groupe d'alimentation en pression (10).
  5. Dispositif de protection selon la revendication 4, caractérisé en ce que la vanne-pilote (47') commandée par pression et prévue pour l'alimentation de la seconde chambre de commande (37) de la vanne-pilote (31) avec la pression de comparaison (PV) est conformée en vanne à commande différentielle qui, par alimentation d'une première chambre de commande (49') avec la pression de sortie (PH) de la pompe principale (42), peut être amenée dans la position de fonctionnement (I) qui provoque l'alimentation de la seconde chambre de commande (37) de la vanne-pilote (31) avec la pression de comparaison (PV), et qui, par alimentation en pression d'une seconde chambre de commande (52), peut être amenée dans la position de base (0) qui provoque la décharge de la seconde chambre de commande (37) de la vanne-pilote (31).
  6. Dispositif de protection selon l'une des revendications 1 à 5, caractérisé en ce que les trajets d'écoulement (53 et 54) actifs dans les positions de fonctionnement alternatives (0 et I) de la vanne-pilote (47, 47') subissent une augmentation progressive de la section de passage au fur et à mesure que le corps de vanne s'écarte de la zone de commutation.
  7. Dispositif de protection selon l'une des revendications 1 à 6, caractérisé en ce que la vanne-pilote (47, 47') est conformée en distributeur à 3/3 voies qui présente, entre la position de fonctionnement (0) dans laquelle la seconde chambre de commande (37) de la vanne-pilote (31) est bloquée par rapport à la prise de pression de comparaison (19) du circuit d'utilisation principal (11, 18), mais mise en communication avec le réservoir (32) du groupe d'alimentation en pression (10), et la position de fonctionnement (I) dans laquelle la seconde chambre de commande (37) de la vanne-pilote (31) est reliée à la prise de pression de comparaison (19) du circuit d'utilisation principal mais bloquée par rapport au réservoir (32) du groupe d'alimentation en pression (10), une position de fonctionnement de blocage (II) dans laquelle la seconde chambre de commande (37) de la vanne-pilote (31) est bloquée aussi bien par rapport à la prise de pression de comparaison (19) du circuit d'utilisation principal (11, 18) que par rapport au réservoir (32) du groupe d'alimentation en pression (10).
  8. Dispositif de protection selon la revendication 7, caractérisé en ce que, vu dans la direction de déplacement du corps de vanne, les positions de commutation dans lesquelles la vanne-pilote (47, 47') est amenée de sa position de fonctionnement de blocage (II) à sa position de passage (0) ou à sa position de passage (I) alternative, sont disposées les unes par rapport aux autres à une distance située entre 1/50 et 1/5, de préférence autour de 1/10 de la course totale que le corps de vanne peut effectuer entre ses positions de fin de course associées aux positions de passage alternatives (0 et I).
  9. Dispositif de protection selon l'une des revendications 1 à 8, la résistance hydraulique supplémentaire du circuit d'utilisation secondaire étant réalisée sous la forme d'un utilisateur à vitesse de rotation synchrone, caractérisé en ce qu'en régime stationnaire du circuit d'utilisation principal (11, 18), la chute de pression sur la résistance hydraulique réglable (46) du circuit d'utilisation secondaire (46, 44) est égale à 5 % à 15 %, de préférence à 10 %, de la chute de pression se produisant sur l'utilisateur (44) à vitesse de rotation synchrone du circuit d'utilisation secondaire.
EP92905344A 1991-05-14 1992-02-27 Dispositif de protection contre les surcharges pour un moteur d'entrainement d'une pompe principale d'une unite hydraulique d'alimentation en pression Expired - Lifetime EP0584078B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4115606 1991-05-14
DE4115606A DE4115606A1 (de) 1991-05-14 1991-05-14 Ueberlast-schutzeinrichtung fuer einen als brennkraftmaschine ausgebildeten antriebsmotor einer hauptpumpe eines hydraulischen druckversorgungsaggregats
PCT/EP1992/000424 WO1992020921A1 (fr) 1991-05-14 1992-02-27 Dispositif de protection contre les surcharges pour un moteur d'entrainement, se presentant sous la forme d'un moteur a combustion interne, d'une pompe principale d'une unite hydraulique d'alimentation en pression

Publications (2)

Publication Number Publication Date
EP0584078A1 EP0584078A1 (fr) 1994-03-02
EP0584078B1 true EP0584078B1 (fr) 1995-01-11

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EP92905344A Expired - Lifetime EP0584078B1 (fr) 1991-05-14 1992-02-27 Dispositif de protection contre les surcharges pour un moteur d'entrainement d'une pompe principale d'une unite hydraulique d'alimentation en pression

Country Status (6)

Country Link
US (1) US5421705A (fr)
EP (1) EP0584078B1 (fr)
JP (1) JP3319753B2 (fr)
DE (2) DE4115606A1 (fr)
ES (1) ES2068706T3 (fr)
WO (1) WO1992020921A1 (fr)

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JPH08338405A (ja) * 1995-04-12 1996-12-24 Komatsu Ltd 可変容量型油圧ポンプの容量制御装置
DE19724870A1 (de) * 1997-06-12 1998-12-17 Bosch Gmbh Robert Verstellbare hydraulische Arbeitsmaschine
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Also Published As

Publication number Publication date
ES2068706T3 (es) 1995-04-16
US5421705A (en) 1995-06-06
DE59201202D1 (de) 1995-02-23
JPH06507219A (ja) 1994-08-11
DE4115606A1 (de) 1992-11-19
JP3319753B2 (ja) 2002-09-03
EP0584078A1 (fr) 1994-03-02
WO1992020921A1 (fr) 1992-11-26

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