EP0284988B1 - Regeleinrichtung für wenigstens zwei mit einer gemeinsamen Arbeitsdruckleitung in Verbindung stehenden hydrostatischen Maschinen - Google Patents

Regeleinrichtung für wenigstens zwei mit einer gemeinsamen Arbeitsdruckleitung in Verbindung stehenden hydrostatischen Maschinen Download PDF

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Publication number
EP0284988B1
EP0284988B1 EP88104661A EP88104661A EP0284988B1 EP 0284988 B1 EP0284988 B1 EP 0284988B1 EP 88104661 A EP88104661 A EP 88104661A EP 88104661 A EP88104661 A EP 88104661A EP 0284988 B1 EP0284988 B1 EP 0284988B1
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EP
European Patent Office
Prior art keywords
pressure
regulator
machine
regulating device
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
EP88104661A
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German (de)
English (en)
French (fr)
Other versions
EP0284988A3 (en
EP0284988A2 (de
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
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Filing date
Publication date
Application filed by Brueninghaus Hydraulik GmbH filed Critical Brueninghaus Hydraulik GmbH
Publication of EP0284988A2 publication Critical patent/EP0284988A2/de
Publication of EP0284988A3 publication Critical patent/EP0284988A3/de
Application granted granted Critical
Publication of EP0284988B1 publication Critical patent/EP0284988B1/de
Anticipated expiration legal-status Critical
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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 approximately 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.
  • the pumps are deliberately set to slightly different controller characteristics.
  • the first pump regulates eg at 200 bar, the second at 205 bar and the third at 210 bar.
  • the load is thus clearly defined and the pendulum is avoided, although the pumps are subject to different wear due to different loads.
  • an increase in pressure in stages is predetermined in this known method.
  • 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.
  • the one machine is a leading machine and the at least one other machine is a slave machine.
  • the control of the other machine includes a control signal dependent on its volume setting as the actual value and a control signal dependent on the volume setting of the one machine as the target value .
  • the at least one other machine is regulated as a function of the volume setting of the one machine, which results in the desired parallel or parallel operation.
  • the embodiment according to claim 6 leads to a simple and practical construction in machines with reversible throughput direction.
  • the design according to claim 7 includes simple and practical features for remote control of the pressure regulator.
  • the pumps 1, 2 of the drive unit are of the same basic equipment, and they each have a controller 3, 4 for their adjusting device and a control means 5, which one of the delivery rate setting associated pumps 1, 2 dependent control signal X is generated.
  • the controllers 3 are each formed by a pressure compensator.
  • the adjusting device comprises a hydraulic cylinder 6 with an adjusting piston 7, which adjusts the associated pump 1, 2 against a compression spring 9 arranged in the piston ring space 8 in the direction of low delivery or zero position and in the opposite direction in the direction of maximum delivery.
  • the piston chamber 11 of the cylinder 6 is connected by a connecting line 12 to a working pressure line section 13 of the associated pump 1, 2, the working pressure line sections 13 being connected to a common working pressure line 14 leading to a consumer B.
  • the control valve 15 of the controller 3 formed by the pressure compensator is arranged in the connecting line 12.
  • the control means 5 is formed in the present embodiment by a pressure control valve, here a pressure relief valve 17, the slide 16 of which is adjustable via a valve spring 18 by a plunger 19 which scans an inclined surface 21 on the adjusting piston 7.
  • the piston annulus 8 is connected by a line 10 to the connecting line 12 and is therefore subjected to working pressure.
  • the regulator 3 is a pressure regulator with a proportional valve, the slide 16 of which can be acted upon by the working pressure against a valve spring 23 adjustable spring force via a line section 22 starting from the connecting line 12. Against that is Slider 16 of the regulator 4 is acted upon by the control signal X ist1 generated by the associated pressure relief valve 17 as the actual value and on the other hand by the valve spring 23 and the control signal X generated by the pressure relief valve 17 of the first pump as the setpoint.
  • both pressure limiting valves 17 are connected on the input side to the connecting line 12 by means of line sections 24, a throttle 25 being arranged in the line sections 24 and, on the other hand, connected to the outlet.
  • a connecting line 26 branches off from the line section 24 of the pump 2, via which the slide 16 of the regulator 4 can be acted upon by the control signal X ist1 defining the delivery rate setting of the pump 2.
  • branches off from the line section 24 of the pump 1 downstream of the throttle 25 is a connection line 27 from by means of which and by means of a branching-off in front of her line section 28, the control valve 15 of the pump 2, as described above with the delivery setting of the pump 1 defining pressure signal X is intended as a target value X is acted upon.
  • the control valves 15 are basically the same valves, the function of which is determined either by connection to the working pressure (pump 1) or by connection to the pressure signal X1 (pump 2).
  • the working pressure is weighed against the force of valve spring 23 (regulator setting) on the pressure compensator forming regulating valve 15.
  • the pressure signal X ist1 forming the actual value is weighed against the force of the valve spring 23 and the pressure signal X forming the setpoint X soll is weighed.
  • the arrangement of an adjustable throttle 29 in a connecting the connecting line 12 between the cylinder 7 and the control valve 15 with the associated drain line 31 Cross line 32 and a parallel line 30 starting from the control valve 15 are the same for both control valves 15.
  • a delivery rate setting of the pump 2 as a function of the delivery rate setting of the pump 1, that is to say a parallel or synchronous operation, the parallelism or the synchronous operation being effected by changing the force of the valve spring 18 and / or the valve spring 23 of controller 4 can be set.
  • the delivery rate settings of pumps 1, 2 and their swivel angle a can be set equally.
  • the pump 1 thus represents a lead pump, while the pump 2 is a slave pump. In this way, the same delivery rate setting of the pumps 1, 2 can be achieved without a significant pressure increase in the controller characteristic. An essentially constant working pressure is thus maintained in the control range.
  • the drive unit to more than one pump 2, which is dependent on the situation. This is indicated by a further working pressure line section 13 and a further connecting line 27 in each case at 33.
  • One or more secondary pumps 2 can thus be regulated by a control means 2, here the pressure relief valve 17 of the lead pump 1. If the lead pump 1 fails, one of the slave pumps 2 can easily be converted into a lead pump.
  • the pressure regulator 3 of the lead pump 1 can be easily converted into a remotely controllable embodiment, as shown in FIG. 2.
  • a connecting line 35 is arranged, which starts from the connecting line 12 carrying the working pressure and to the slide 16 of the regulator 3 on the Leads on which the valve spring 23 (compression spring) is arranged.
  • a line 37 branches off to the outlet behind a throttle 36, in which a remote control valve 38 formed by a pressure control valve is arranged.
  • the pressure limiting valves 17 are preferably connected to the working pressure line 14 via a common pressure reducing valve 41 arranged in a connecting line 40, the pressure limiting valves 17 being connected to the pressure reducing valve 41 via line sections 43 containing throttles 42.
  • the control signal X is to the controller 4 of the lag pump 2-transmitting connection line 44 branches off between the throttle 42 and the pressure relief valve 17 of the line section 43 of the transfer pump 1 and is arranged similar to the first embodiment.
  • the connecting line 45 transmitting the control signal X ist1 to the controller 4 branches off between the throttle 42 and the pressure limiting valve 17 from the line section 43 of the sequence pump 2.
  • the embodiment shown in Fig. 4 differs from the above in that the control means 5 are formed by pressure reducing valves 50, a flow control signal dependent from the working pressure X is or X generate IST1 and this, urged by the plungers 19, depending on the accompanying Flow rate control will.
  • the pressure reducing valve 50 of the lead pump 1 is arranged in a line 51 which starts from the connecting line 12 carrying the working pressure and is connected via at least one line section 52 to the regulator 4 of the follow-up pump 2 on the spring 23 side or to further follow-up pumps 2 is.
  • the explanations according to fig. 3 and 4 have lower power loss due to the use of the pressure reducing valves 41 and 50, in particular at high working pressures.
  • FIG. 5 shows, as an exemplary embodiment, a sectional view of a pressure control valve on an enlarged scale, which can be used as a pressure limiting valve 17 in the exemplary embodiment according to FIGS. 1 to 3 and, in principle, also in the exemplary embodiment according to FIG. 4.
  • the actuating element 19 acts by means of the one hand supported on him and on the other hand engaging on the slide 16 spring 18 on the slider 16 of the pressure relief valve 17, which is the control signal X by means of control edges 61 and X IST1 adjusts.
  • the valve housing 64 is screwed into the housing of the cylinder 6 or an attachment part thereof.
  • the slider 16 is located in an adjusting bush 65, which can be adjusted axially in the valve housing 64 by means of a thread 66 by turning an attack element, here a hexagon socket 67, and can be locked by means of a lock nut 68 screwed onto the adjusting bush 65.
  • An input throttle 72 is arranged between the connection 69 and a transverse bore 71 which intersects the bore 62 in the adjusting bush 65, and the throttle 25 according to FIG. 1 and 2 or the throttle 42 according to FIG. 3 corresponds. In the exemplary embodiment according to FIG. 4, such a throttle is not required.
  • control signals X ist and X ist1 can also be formed using a control pressure be generated, for example, in a manner known per se by an auxiliary pump.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)
EP88104661A 1987-04-02 1988-03-23 Regeleinrichtung für wenigstens zwei mit einer gemeinsamen Arbeitsdruckleitung in Verbindung stehenden hydrostatischen Maschinen Expired - Lifetime EP0284988B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3711053 1987-04-02
DE19873711053 DE3711053A1 (de) 1987-04-02 1987-04-02 Regeleinrichtung fuer wenigstens zwei mit einer gemeinsamen arbeitsdruckleitung in verbindung stehende hydrostatische maschinen

Publications (3)

Publication Number Publication Date
EP0284988A2 EP0284988A2 (de) 1988-10-05
EP0284988A3 EP0284988A3 (en) 1989-12-27
EP0284988B1 true EP0284988B1 (de) 1992-12-16

Family

ID=6324677

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88104661A Expired - Lifetime EP0284988B1 (de) 1987-04-02 1988-03-23 Regeleinrichtung für wenigstens zwei mit einer gemeinsamen Arbeitsdruckleitung in Verbindung stehenden hydrostatischen Maschinen

Country Status (2)

Country Link
EP (1) EP0284988B1 (enrdf_load_stackoverflow)
DE (2) DE3711053A1 (enrdf_load_stackoverflow)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4025638C1 (enrdf_load_stackoverflow) * 1990-08-13 1991-12-05 Brueninghaus Hydraulik Gmbh, 7240 Horb, De
DE4118869C2 (de) * 1991-06-07 1995-06-29 Hydromatik Gmbh Regelvorrichtung zur Regelung des Verdrängungsvolumens mehrerer hydrostatischer Maschinen
DE19626793C1 (de) * 1996-07-03 1997-06-26 Brueninghaus Hydromatik Gmbh Hydraulische Regeleinrichtung zum parallelen Regeln mehrerer hydrostatischer Verstellpumpen
DE102015000869B4 (de) * 2015-01-23 2019-10-24 Dürr Systems Ag Pumpenanordnung und entsprechendes Betriebsverfahren
AT524891B1 (de) * 2021-03-29 2023-01-15 Engel Austria Gmbh Hydraulische Antriebsvorrichtung für eine Formgebungsmaschine

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1056655A (en) * 1964-11-16 1967-01-25 Ifield & Sons Pty Ltd R J Torque control means for variable displacement hydraulic pumps
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 (en) * 1977-02-24 1981-06-30 Commercial Shearing, Inc. Pressure and flow compensated control system with constant torque and viscosity sensing over-ride
DE3345264A1 (de) * 1983-12-14 1985-06-27 Brueninghaus Hydraulik Gmbh, 7240 Horb Drehmomenten-regeleinrichtung fuer eine verstellbare hydropumpe

Also Published As

Publication number Publication date
DE3876661D1 (de) 1993-01-28
DE3711053C2 (enrdf_load_stackoverflow) 1992-01-30
EP0284988A3 (en) 1989-12-27
EP0284988A2 (de) 1988-10-05
DE3711053A1 (de) 1988-10-20

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