EP0284989B1 - Régulateur pour au moins deux machines hydrostatiques communiquant par une conduite sous pression commune - Google Patents

Régulateur pour au moins deux machines hydrostatiques communiquant par une conduite sous pression commune Download PDF

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Publication number
EP0284989B1
EP0284989B1 EP88104662A EP88104662A EP0284989B1 EP 0284989 B1 EP0284989 B1 EP 0284989B1 EP 88104662 A EP88104662 A EP 88104662A EP 88104662 A EP88104662 A EP 88104662A EP 0284989 B1 EP0284989 B1 EP 0284989B1
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EP
European Patent Office
Prior art keywords
pressure
control
valve
regulator according
adjusting
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
EP88104662A
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German (de)
English (en)
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EP0284989A3 (en
EP0284989A2 (fr
Inventor
Gerhard Beutler
Hermann Maier
Clemens Krebs
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.)
Brueninghaus Hydraulik GmbH
Original Assignee
Brueninghaus Hydraulik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19873711049 external-priority patent/DE3711049A1/de
Application filed by Brueninghaus Hydraulik GmbH filed Critical Brueninghaus Hydraulik GmbH
Publication of EP0284989A2 publication Critical patent/EP0284989A2/fr
Publication of EP0284989A3 publication Critical patent/EP0284989A3/de
Application granted granted Critical
Publication of EP0284989B1 publication Critical patent/EP0284989B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04B49/08—Regulating by delivery pressure

Definitions

  • the invention relates to a control device according to the preamble of claim 1.
  • the delivery rate settings of the pumps are indefinite because, due to the roughly constant working pressure, no relationship can be derived that would ensure a uniform delivery rate setting for all pumps, i.e. parallel operation. Therefore, the pumps can take any delivery settings at any time, e.g. one pump can be in maximum and the other pump in minimum delivery setting. This has the following disadvantages.
  • the pumps oscillate at a swivel angle, even if the total amount delivered does not change. This results in losses and noises.
  • the second pump swallows the flow rate that the first pump delivers. This results in increased wear and power loss and is associated with high noise levels.
  • EPC EP-A 0232722 a control device for the power control of several hydraulic pumps driven by a drive machine is described. It is not concerned with the uniform delivery rate setting of the various hydraulic pumps operating in a common working pressure system of constant pressure.
  • the invention has for its object to design a control device of the type mentioned in such a way that, while ensuring a uniform load on the machines, hydraulic synchronous operation or parallel operation is achieved with one another.
  • an additional control signal is included in the control, which is generated as a function of the volume setting of the associated machine and is given to the pressure regulator.
  • the synchronism of the pumps achieved by the design according to the invention results from the fact that, depending on the control signal, which is dependent on the volume setting of the associated machine, a control characteristic, which is progressive or degressive and can be selected in terms of its steepness, is specified which, in terms of effectiveness, has the same working pressure at all Pressure regulator allows the same delivery rate setting.
  • the synchronous operation or parallel operation is achieved without a significant increase in pressure in the working pressure.
  • a constant working pressure is achieved in all operating states, since the control valve is acted upon directly or exclusively as a function of the working pressure, the synchronous delivery rate setting of the pumps being guaranteed by the fact that the control oil amount for the pressure regulators is divided by the control means depending on the delivery rate setting, which results in correction signals for the pressure regulator for the purpose of induction a loading of the adjusting devices ensuring synchronism.
  • control valve or valves e.g. with regard to their control edges, set the control pressure proportionally or inversely proportional to the deviation of the working pressure from the value set with the control valve.
  • the design according to claim 9 includes simple and practical features for remote control of the pressure regulator.
  • the embodiment according to claim 11 leads to a simple and practical construction in machines with reversible throughput direction, e.g. with reversible swivel direction for mooring or motor operation.
  • the pumps denoted by 1 are connected by line sections 2 to a common working pressure line 3 leading to a consumer B, the number of pumps being able to be increased as desired, which is illustrated by the position symbol 4, which denotes connections for further possible pumps.
  • the pump units are identical to one another.
  • Each adjusting device 5 of the pumps 1 is assigned a pressure regulator 6 with a proportional control valve 7 in the form of a pressure compensator, the slide 8 of which regulates the passage of a connecting line 9 which starts from the associated working pressure line section 2 and opens into the piston chamber 10 of a cylinder 11 of the adjusting device 5 .
  • the slide 8 can be acted upon on the one hand by a line section 12 with the working pressure and on the other hand by a line section 13, in which a throttle 14 is arranged, with a reduced pressure.
  • This pressure acts in the same direction with a valve spring 15 acting on the valve slide 8, the spring force of which is optionally adjustable.
  • the piston annular space 16 of the cylinder 11, in which a compression spring 17 is arranged for the purpose of resetting the adjusting device 5, is connected to the connecting line 9 by a line section 18 and can thus be subjected to the working pressure.
  • the pressure regulator 6 described so far, including a 19, optionally adjustable nozzle in a discharge line 20 extending from the piston chamber 10 and a parallel line 21 connected to the latter, originating from the control valve 7, is of a conventional type and is therefore known, so that a functional description is dispensed with in detail can be.
  • the pressure regulators 6 set a working pressure which, apart from a slight change in pressure, essentially is to be regarded as constant.
  • the slight change in pressure in the working pressure in the control range of the pressure regulator 6 is caused by the progressive characteristic of the springs 15 and 17 as well as the friction and self-adjusting forces of the adjusting device 5 and is about 3 bar in the case of conventional pressure regulators 6.
  • each pump 1 is assigned a control means, generally designated 25, which acts on the pressure regulator 6 with a control signal which is dependent on the respective delivery rate setting of the associated pump 1. 1 and 2, the control means 25 is formed by a pressure relief valve 26, which is arranged in a line 27 branching off from the line section 13, preferably behind the throttle 14, and the control pressure p St present in the line section 13 as a function of the delivery rate setting of the associated one Pump 1 controls.
  • An actuator 28 in the form of a feeler pin is used to transmit the respective setting for the delivery rate setting, which at one end bears against an inclined surface 31 on the adjusting piston 29 of the cylinder 11 outside the latter and acts by means of a spring 32 on the slide of the pressure limiting valve 26 and against it Inclined surface 31 is applied.
  • the adjusting element 28 is mounted in its longitudinal direction so that it performs a longitudinal movement when the adjusting piston 29 is displaced longitudinally, whereby it acts on the pressure limiting valve 26.
  • the arrangement in the present exemplary embodiment is such that the pressure limiting valve 26 closes when the adjusting device 5 is pivoted in, that is to say when the adjusting piston 29 is moved to the left, as a result of which the control pressure p St is increased, ie a pressure signal X is generated which corresponds to the Slider 8 of the control valve 7 against Working pressure applied.
  • the working pressure at the control valve 7 is no longer only in equilibrium with the force of the spring 15 (controller setting), but the controller setting increases as a function of the pivoting angle a by the pressure signal X. This results in a pressure increase and a pressure increase in the pivoting in Controller characteristic.
  • the delivery rate setting of the pumps 1 is determined when the working pressure acting on the pressure regulators 6 is essentially the same, which results in the same delivery rate setting for the pumps 1 during operation of the pumps 1, ie parallel or synchronous operation.
  • An effective pressure increase with regard to the desired synchronization is given when the pressure rises above the setting range of above approximately 10 bar. Very good results are achieved with a pressure increase of 20 bar.
  • the configuration according to the invention is also suitable for pumps which can be adjusted in both delivery directions.
  • FIG. 2 shows, as an exemplary embodiment, a sectional view of a pressure limiting valve 26 in an enlarged view.
  • the actuating element 28 acts by means of the spring 32, which is supported on it on the one hand and engages on the slide 33 on the other hand, on the slide 33 of the pressure limiting valve 26, which regulates the control pressure p St , ie a control signal X, by means of control edges 34.
  • the valve housing 38 is screwed into the housing of the cylinder 11 or an attachment part of the same.
  • the slide 33 is located in an adjusting bush 39, which can be adjusted axially in the valve housing 38 by means of a thread 41 by turning an attack element, here a hexagon socket 42, and can be locked by means of a lock nut 43 screwed onto the adjusting bush 39.
  • An input throttle 45 which corresponds to the throttle 14 according to FIG. 1, is arranged between the connection 35, which can be connected to the line 27 in FIG. 1, and a transverse bore 44 which intersects the bore 36 in the adjusting bushing 39.
  • control means 25 are formed by means of the adjusting element 28 against a spring 48 adjustable throttles 49, the outputs of which via branch lines 5) a remote control valve 51 is connected, which is formed by a pressure control valve which is connected to the drain. All pressure regulators 6 can be controlled simultaneously by means of the remote control valve 51. Between the respective branch line 5) and line 27, when the throttle 49 is completely open in the working position shown, there is a pressure difference d which is dependent on the delivery rate setting, i.e. in the present case from the swivel angle a.
  • each pump 1 is assigned a control means, generally designated 25, which throttles the amount of control oil that flows through lines 27, 58, depending on the respective delivery rate setting of the associated pump 1.
  • the control means 25 is formed by an adjustable throttle 59, which in the line section 13 is preferably behind the throttle 14 branching line 27 is arranged and controls the amount of control oil flowing in the line section 13 or 27 depending on the delivery rate setting of the associated pump 1.
  • the throttles 59 are each connected on the output side through the line section 58 to a common return line 61, in which a preferably remotely controllable pressure control valve 62 is arranged, which in the present exemplary embodiment is a pressure connection valve.
  • the pressure control valve 62 is connected by a control line 63 to the working pressure line 3 and is controlled by the working pressure in such a way that it reduces the control pressure p St1 in the line sections 27 and the control pressure p St2 reduced by a pressure difference d ( dynamic pressure) determined by the throttle 59 Line sections 58 or in the return line 61 is lowered towards the return when the working pressure exceeds the control pressure set on the control valve 62, preferably with the control spring.
  • the pump units are identical to one another, i.e. same pressure regulator 6 with the same spring setting 15 and same constant throttles 14 and same adjusting throttles 59 with the same throttle dependence on the swivel angle a.
  • control element 33 is also used to transmit the stipulation corresponding to the respective delivery quantity setting.
  • the actuating element 33 bears against the inclined surface 34 on the adjusting piston 30 of the cylinder 11 and is acted upon by a spring against the inclined surface 34.
  • the adjusting element 33 is mounted in its longitudinal direction so that it performs a longitudinal movement when the adjusting piston 30 is displaced longitudinally, whereby it acts on the throttle 59 or on the slide of the throttle valve.
  • the arrangement is in the present embodiment so that the throttle 59 closes when the adjusting device 5 is pivoted in , ie when the adjusting piston 30 is moved to the left, as a result of which the control pressure p St1 is increased because the amount of control oil decreases and the control pressure at the throttle 14 is reduced, ie it a pressure signal X is generated, which acts on the slide 8 of the control valve 7 against the working pressure.
  • This means that the working pressure at the control valve 7 is no longer in equilibrium with the force of the spring 16 (controller setting), but the controller setting initially increases by the pressure signal X as a function of the delivery rate setting or the swivel angle a.
  • control device The following functional details of the control device are described briefly below, in particular according to FIG. 4.
  • the amount of control oil flowing through lines 13, 27, 58 to the pressure control valve 62 of the pressure regulators 6 flows through the lines 13 via the constant throttles 14 for each individual regulator of the at least two pumps 1.
  • a back pressure is set at the throttle 14.
  • the dynamic pressure acts on the valve slide 8 against the spring force of the spring 15.
  • valve slide 8 In order to regulate the adjusting piston 30 in any pivot position between the respective end stops 22, it is necessary for the valve slide 8 to assume a central position in which the spring force of the spring 15 and the opposing dynamic pressure of the throttle 14 are in equilibrium, and the connecting line 9 and the parallel or return line 21 are in throttled connection with the actuating piston chamber 10.
  • valve slide 8 moves against the spring force due to increasing dynamic pressure at the throttle 14 and opens the connection from line 9 to the adjusting cylinder 11. As a result, the pump pivoting angle a is reduced to zero. If the amount of control oil is smaller, the pump swivel angle a increases towards the maximum.
  • control oil quantities are combined in lines 61 and regulated by the pressure control valve 62 as a function of the operating pressure.
  • the pressure control valve 62 closes so that the control oil quantity decreases and the delivery quantity of the pumps increases and the operating pressure increases.
  • the pressure control valve 62 opens, so that the control oil quantity increases and the delivery quantity of the pumps decreases and the operating pressure drops.
  • the pressure balance at the pressure control valve 62 depends only on the operating pressure in the connecting line 32 and the spring setting and is independent of the swivel angle ⁇ of the pumps 1.
  • the distribution of the control oil quantity regulated by the pressure control valve 62 to the individual pumps depends, since the constant throttles 14 are the same, only on the position of the adjusting throttles-59.
  • the throttles 59 close at a minimum flow rate and open at a maximum flow rate and enable a continuous throttle change in the intermediate positions.
  • the control oil quantity of the pump 1 with the largest swivel angle a is the largest
  • the control oil quantity of the pump 1 with the smallest swivel angle a is the smallest. Since with all pressure regulators 6 the required control oil quantity is the same at the control point, pump 1 with the larger control oil quantity (larger swivel angle a) must swivel in and pump 1 with the smaller control oil quantity (smaller swivel angle a) swivel out until swivel angle a is equal and the control oil quantities are evenly divided by the adjusting throttles 59.
  • the configuration according to the invention is also suitable for pumps or motors which can be set in both directions of delivery.

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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)
  • Operation Control Of Excavators (AREA)

Claims (11)

  1. Régulateur pour au moins deux machines hydrostatiques à volume de refoulement et/ou d'aspiration variable, communiquant par une conduite sous pression commune, dans lequel est associé à chaque machine un dispositif variateur de réglage avec un piston hydraulique variateur de réglage, et un régulateur de pression pour le réglage volumétrique des machines et pour le maintien de la pression de travail à une valeur constante,
    caractérisé en ce qu'à chaque régulateur de pression (6) est associé un moyen de commande (25) qui fait varier le régulateur de pression (6) avec un signal de commande dépendant du réglage volumétrique momentané de la machine (1) correspondante, proportionnellement au réglage volumétrique.
  2. Régulateur selon la revendication 1, caractérisé en ce que le moyen de commande (25) peut être commandé par un organe de mesure de trajet coopérant avec le dispositif variateur de réglage (5) ou avec un élément assemblé à celui-ci.
  3. Régulateur selon la revendication 2, caractérisé en ce que l'organe de mesure de trajet est constitué par une portée oblique (31) sur une partie du dispositif variateur de réglage (5), de préférence sur le piston variateur de réglage (29) et par un élément de réglage (28) qui palpe la portée oblique (31).
  4. Régulateur selon une des revendications 1 à 3, caractérisé en ce que le moyen de commande (25) est constitué par une vanne à étranglement réglable (49) qui est disposée dans une conduite de commande (27,50) servant à solliciter le régulateur de pression (6).
  5. Régulateur selon une des revendications 1 à 4, caractérisé en ce que le moyen de commande (25) est une vanne régulatrice de pression, en particulier une vanne (26) limitant la pression, ou une vanne réductrice de pression.
  6. Régulateur selon la revendication 4 ou 5, caractérisé en ce que la conduite de commande (27,58) communique avec le circuit de retour par au moins une vanne de régulation (62) réglant la pression de commande (PSt1, PSt2) contenue dans celle-ci.
  7. Régulateur selon la revendication 6, caractérisé en ce que la vanne de régulation (62) est sollicitée par la pression de travail ou par une pression dépendant de celle--ci, et alors, quand la pression de travail s'écarte de la valeur réglée par la vanne de régulation, diminue ou augmente la pression de commande (PSt1, PSt2) de manière proportionnelle ou inversement proportionnelle à cet écart, de préférence en diminuant ladite pression de commande dans le cas d'une augmentation de la pression de travail au dessus de la valeur sur laquelle elle est réglée.
  8. Régulateur selon la revendication 7, caractérisé en ce que la vanne régulatrice (62) est une vanne interrompant la pression.
  9. Régulateur selon la revendication 7 ou 8, caractérisé en ce que la vanne régulatrice (62) est une vanne de commande à distance.
  10. Régulateur selon une des revendications 7 à 9, caractérisé en ce qu'une vanne régulatrice commune (62) est disposée dans une conduite de retour commune (61).
  11. Régulateur selon une des revendications 2 à 10, caractérisé en ce que les machines (1) sont agencées pour fonctionner dans les deux sens de circulation et en ce que les organes de mesure de trajet se trouvent dans leurs positions médianes quand les dispositifs variateurs de réglage (5) sont en position zéro.
EP88104662A 1987-04-02 1988-03-23 Régulateur pour au moins deux machines hydrostatiques communiquant par une conduite sous pression commune Expired - Lifetime EP0284989B1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE3711049 1987-04-02
DE19873711049 DE3711049A1 (de) 1987-04-02 1987-04-02 Regeleinrichtung fuer wenigstens zwei mit einer gemeinsamen arbeitsdruckleitung in verbindung stehende hydrostatische maschinen
DE19873742111 DE3742111A1 (de) 1987-04-02 1987-12-11 Regeleinrichtung fuer wenigstens zwei mit einer gemeinsamen arbeitsdruckleitung in verbindung stehende hydrostatische maschinen veraenderlichen foerder- bzw. schluckvolumens
DE3742111 1987-12-11

Publications (3)

Publication Number Publication Date
EP0284989A2 EP0284989A2 (fr) 1988-10-05
EP0284989A3 EP0284989A3 (en) 1989-12-27
EP0284989B1 true EP0284989B1 (fr) 1992-03-18

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP88104662A Expired - Lifetime EP0284989B1 (fr) 1987-04-02 1988-03-23 Régulateur pour au moins deux machines hydrostatiques communiquant par une conduite sous pression commune

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EP (1) EP0284989B1 (fr)
DE (2) DE3742111A1 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19626793C1 (de) * 1996-07-03 1997-06-26 Brueninghaus Hydromatik Gmbh Hydraulische Regeleinrichtung zum parallelen Regeln mehrerer hydrostatischer Verstellpumpen
EP3045723B1 (fr) * 2015-01-16 2019-04-10 HAWE Hydraulik SE Pompe à pistons axiaux

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0232722A2 (fr) * 1986-01-11 1987-08-19 Hitachi Construction Machinery Co., Ltd. Méthode et sysème de réglage pour contôler la puissance d'entrée des pompes hydrauliques d'un système hydraulique

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3067693A (en) * 1958-12-24 1962-12-11 United Aircraft Corp Control means for variable delivery pump
DE1188948B (de) * 1960-07-16 1965-03-11 Metallwerk Glockerau G M B H Arbeitsfluessigkeitsmengen-Regeleinrichtung fuer hydrostatische Pumpen und Motoren
DE1921298B2 (de) * 1969-04-25 1973-08-23 Hydromatik Gmbh, 7900 Ulm Einrichtung zur regelung der foerdermenge verstellbarer axialkolbenpumpen
US4055046A (en) * 1976-12-22 1977-10-25 Caterpillar Tractor Co. Control system having override for fluid operated work elements
CA1104033A (fr) * 1977-02-24 1981-06-30 Commercial Shearing, Inc. Dispositif de commande a compensation de pression et de debit, a couple constant et element de detection de viscosite
US4087968A (en) * 1977-04-28 1978-05-09 Caterpillar Tractor Co. Flow control valve for combining two dissimilar independent systems to a common pressure source
DE3345264A1 (de) * 1983-12-14 1985-06-27 Brueninghaus Hydraulik Gmbh, 7240 Horb Drehmomenten-regeleinrichtung fuer eine verstellbare hydropumpe

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0232722A2 (fr) * 1986-01-11 1987-08-19 Hitachi Construction Machinery Co., Ltd. Méthode et sysème de réglage pour contôler la puissance d'entrée des pompes hydrauliques d'un système hydraulique

Also Published As

Publication number Publication date
DE3742111A1 (de) 1989-06-29
EP0284989A3 (en) 1989-12-27
DE3869165D1 (de) 1992-04-23
EP0284989A2 (fr) 1988-10-05

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