EP0391097B1 - Vorrichtung zum Regeln des Betriebs von Hydromotoren - Google Patents

Vorrichtung zum Regeln des Betriebs von Hydromotoren Download PDF

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Publication number
EP0391097B1
EP0391097B1 EP90104817A EP90104817A EP0391097B1 EP 0391097 B1 EP0391097 B1 EP 0391097B1 EP 90104817 A EP90104817 A EP 90104817A EP 90104817 A EP90104817 A EP 90104817A EP 0391097 B1 EP0391097 B1 EP 0391097B1
Authority
EP
European Patent Office
Prior art keywords
hydraulic motor
control valve
flow regulating
regulating valve
pressure medium
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
EP90104817A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0391097A1 (de
Inventor
Alfred Dipl.-Ing. Marian
Mathias Dr.-Ing. Szewczyk
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.)
Paul Pleiger Maschinenfabrik GmbH and Co KG
Original Assignee
Paul Pleiger Maschinenfabrik 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
Application filed by Paul Pleiger Maschinenfabrik GmbH and Co KG filed Critical Paul Pleiger Maschinenfabrik GmbH and Co KG
Publication of EP0391097A1 publication Critical patent/EP0391097A1/de
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Publication of EP0391097B1 publication Critical patent/EP0391097B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
    • F03C1/04—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinders in star or fan arrangement
    • F03C1/0447—Controlling
    • F03C1/0457—Controlling by changing the effective piston stroke
    • F03C1/046—Controlling by changing the effective piston stroke by changing the excentricity of one element relative to another element

Definitions

  • the invention relates to a device for regulating the operation of hydraulic motors according to the preamble of claim 1.
  • a device of this type is known from DE-OS 33 13 974, by means of the control valve when the torque demanded of the hydraulic motor changes, the eccentricity of the motor is adjusted so that the pressure behind the flow control valve or the to avoid power losses pressure applied to the engine is kept constant within narrow limits. By changing the eccentricity and thus the swallowing volume of the motor the speed of the motor is also changed if the pressure medium flow remains the same. In some areas of application of hydraulic motors, however, it is desirable to keep the motor speed constant even with changing torque.
  • the invention has for its object to design a device of the type mentioned in such a way that, despite pressure optimization, the speed of the hydraulic motor can be kept constant with changing torque, the device should have a simple structure.
  • a control pin 7 is slidably guided in a radially extending bore in the cranked section 2 of the shaft 1, which bears with its opposite ends on the inner circumference of the eccentric ring 3, so that relative to an adjusting movement of the eccentric ring 3 the shaft 1 of the control pin 7 is moved by the eccentric ring 3.
  • the control pin 7 is provided on a section with a schematically indicated helical toothing 8, which is in engagement with a corresponding helical toothing 9 on a slide 10, which is guided in the central bore in the shaft 1 and with one end from the free end face of the Wave 1 protrudes.
  • the ring grooves 6,6 ' are connected to pressure medium lines 11,11', which are connected to the connections U1 and U2 of a control valve 12, which has the function of a hydraulically operated 4/3-way valve and on the input side with a return connection T and a connection for the primary pressure supplied by a pump 13 P 1 is provided.
  • the primary pressure P1 is 14 at the end of a control piston in the control valve 12, while the opposite side of the control piston 15 is acted upon by a spring 16 and the pressure P 2 applied to the hydraulic motor.
  • the function and structure of the control valve 12 is described in detail in DE-OS 33 13 974.
  • the primary pressure P1 of the pump 13 is also present at a flow control valve 17, through which the hydraulic motor is allocated the amount of pressure medium required in each case. Behind the flow control valve 17, the pressure P 2 required by the motor prevails in the pressure line 18.
  • a spring-loaded actuator 19 is attached to the flow control valve 17 and is acted upon by the slide 10 of the hydraulic motor. The actuator 19 acts, for example, via a control curve, not shown, on the passage of the flow control valve 17 in such a way that when the actuator 19 is moved, the amount of pressure medium let through the flow control valve is increased or decreased.
  • a pressure limiter in a pressure medium line 21 is designated, by means of which the flow control valve 17 can be preset to a specific quantity of pressure medium in order to preset the speed of the hydraulic motor to a specific value.
  • the device works as follows. In the operating position shown, the hydraulic motor works, for example, with the predetermined speed and a predetermined pressure difference P 1 - P 2 on the flow control valve 17. For example, if the hydraulic motor requires a torque, for example, a stirrer driven by the motor, the operating pressure P 2 required by the motor is first reduced.
  • This change of P2 acts in such a way on the control valve 12 that the eccentricity of the eccentric ring 3 is reduced via the pressure medium lines 11, 11 'and the actuating piston 4.4', so that the engine Required torque and reduced leverage on the eccentric, the operating pressure P2 rises again to a value which corresponds to a predetermined pressure difference P1 - P2, it being assumed that the pressure P1 supplied by the pump 13 is constant. In this way, the pressure difference at the flow control valve 17 is kept constant to avoid power losses via the control valve 12 when the torque changes.
  • the radial adjustment of the eccentric ring 3 which is carried out in this case is transmitted via the control pin 7 into an axial displacement movement of the slide 10, which acts on the flow control valve 17 via the actuator 19 in such a way that the pressure medium quantity allocated by the flow control valve 17 to the hydraulic motor is reduced. If the amount of pressure medium supplied by the flow control valve 17 remained constant with a reduced eccentricity and thus a reduced swallowing volume of the hydraulic motor, the speed of the motor would be increased due to the reduced swallowing volume. Due to the mechanical coupling of the flow control valve 17 with the eccentric adjustment, the amount of pressure medium to the hydraulic motor is reduced in the example described above in such a way that the speed of the motor remains constant, while at the same time the pressure difference at the flow control valve is kept constant.
  • the operating pressure P2 is first increased and thus the eccentricity is increased via the control valve 12, so that the increased torque can be delivered with the pressure P2 remaining constant, while the slide 10 and the actuator 19 increase the torque from the Flow control valve 17 supplied amount of pressure medium is increased such that the speed remains constant with increased eccentricity.
  • the hydraulic motor always works at the same speed and optimal operating pressure.
  • central supply systems in which several hydraulic motors are supplied with pressure medium by a pump 13 each via a control valve 12 and a flow control valve 17, a substantial improvement in efficiency is achieved since the individual hydraulic motors each work with optimal efficiency despite different loads.
  • the power to be installed in a central supply system can be designed more cheaply.
  • control valve 12 could also be achieved via speed sensors, sensors and the like.Electrical components, but this would require a much higher effort than the mechanical coupling described between eccentric adjustment and flow control valve 17, which is very simple and can be carried out inexpensively.
  • a control cam, an inclined surface or the like can also be provided on one of the two components, while a cam, pin or the like is attached to the other component, which is attached to it Control curve interacts.
  • a control groove or the like is preferably provided, similar to the schematically illustrated toothing, so that the slide 10 is displaced in both directions by the adjustment movement of the control pin 7 in both directions, without the need for spring loading of the slide 10 in one direction.
  • the slide 10 can directly with the Actuator 19 of the flow control valve 17 can be coupled. In the embodiment shown schematically, the actuator 19 is acted upon by a spring so that it is held against the slide 10.
  • the same reference numerals as in FIG. 1 are used for identical or corresponding components.
  • the pressure medium lines 5.5 ' are above the grooves 6.6' with pressure medium lines 11.11 'in connection, which are formed in the slide 10, on the extension of which a control valve 12' is arranged, which is of the construction according to DE-OS 38 18 105 corresponds.
  • the central groove 22 in the through bore of the control valve 12 ' is acted on via a line 23 and a rotary union with the primary pressure P1 of the pump 13, while the grooves 24 correspond to the connection T of the control valve 12 in Fig. 1 and with the atmosphere in connection stand.
  • connection U1 and U2 correspond to the staggered mouths of the lines 11 in the slide 10 in the area of these grooves 22,24.
  • control valve 12 ' is an arm of a pivotally mounted control lever 26, the other arm is acted upon by a predetermined ratio by a solenoid 27.
  • the control valve 12 'on the slide 10 is shifted so that the eccentricity is adjusted so that the pressure difference P1 - P2 on in via a corresponding pressure medium through the lines 11,11' and the actuating piston 4,4 ' Fig. 2 flow control valve, not shown, is kept constant within narrow limits.
  • the spring 25 is supported on a schematically indicated component 28 of the motor housing.
  • the slide 10 protrudes over the end face of the control valve 12 ', so that this free end of the slide 10, as in the embodiment according to FIG. 1, can act on an actuator 19 of the flow control valve, not shown.
  • the solenoid 27 can be controlled by corresponding electrical signals so that the adjustment of the eccentricity required for pressure optimization is carried out when the torque changes.
  • Appropriate actuators are provided for this.
  • a speed sensor is indicated schematically, which is connected to a unit 30 for processing the actual and target values.
  • a corresponding unit for actual and target values of the operating pressure is designated by 31.
  • 32 with a slider 10 cooperating sensor for the eccentricity or the swallowing volume of the motor is designated, which is connected to a unit 33 for actual and target values.
  • the device shown schematically in FIG. 2 can also be provided for pressure optimization at a variable speed of the hydraulic motor, so that in this case the slide 10 does not act via an actuator 19 on the flow control valve to keep the speed constant.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Hydraulic Motors (AREA)
EP90104817A 1989-04-03 1990-03-14 Vorrichtung zum Regeln des Betriebs von Hydromotoren Expired - Lifetime EP0391097B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3910728 1989-04-03
DE3910728A DE3910728A1 (de) 1989-04-03 1989-04-03 Vorrichtung zum regeln des betriebes von hydromotoren

Publications (2)

Publication Number Publication Date
EP0391097A1 EP0391097A1 (de) 1990-10-10
EP0391097B1 true EP0391097B1 (de) 1992-10-21

Family

ID=6377726

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90104817A Expired - Lifetime EP0391097B1 (de) 1989-04-03 1990-03-14 Vorrichtung zum Regeln des Betriebs von Hydromotoren

Country Status (6)

Country Link
US (1) US5117634A (enrdf_load_stackoverflow)
EP (1) EP0391097B1 (enrdf_load_stackoverflow)
CA (1) CA2012510A1 (enrdf_load_stackoverflow)
DD (1) DD297486A5 (enrdf_load_stackoverflow)
DE (2) DE3910728A1 (enrdf_load_stackoverflow)
RU (1) RU2013643C1 (enrdf_load_stackoverflow)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4111649A1 (de) * 1991-04-10 1992-10-15 Kloeckner Humboldt Deutz Ag Kreiselregler mit gesteuerter kreiselfrequenz
AT395929B (de) * 1991-07-12 1993-04-26 Koenig Helmut Vorrichtung zum wirken portionierter teigstuecke
FR2695687B1 (fr) * 1992-09-14 1994-12-16 Domine Sa Dispositif d'asservissement hydraulique pour moteurs d'entraînement de têtes de forage.
DE10035631C2 (de) * 2000-07-21 2003-01-30 Brueninghaus Hydromatik Gmbh Nullastschaltung
DE102004060198B3 (de) * 2004-12-14 2006-03-30 Pleiger Maschinenbau Gmbh & Co. Kg Verfahren und Vorrichtung zum Steuern des Betriebs eines Radialkolbenmotors
US8113033B2 (en) * 2009-06-08 2012-02-14 Cnh America Llc Method to calibrate a flow balance valve on a windrower draper header
CN118407958B (zh) * 2024-07-03 2024-09-27 江苏恒源液压有限公司 用于定量插入式马达的过载保护方法

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2550966A (en) * 1945-07-27 1951-05-01 Westinghouse Electric Corp Variable displacement pump control mechanism
US3744379A (en) * 1970-04-03 1973-07-10 Lucas Industries Ltd Rotary hydraulic machines
US3987624A (en) * 1973-06-18 1976-10-26 Cooke George H Hydraulic drive control system
DE2461897A1 (de) * 1974-12-31 1976-07-08 Bosch Gmbh Robert Regeleinrichtung fuer eine pumpe
US4325215A (en) * 1977-03-10 1982-04-20 Teijin Seiki Company Limited Hydraulic apparatus
US4103489A (en) * 1977-04-15 1978-08-01 Deere & Company Total power fluid system
DE2720306C2 (de) * 1977-05-06 1986-02-27 Robert Bosch Gmbh, 7000 Stuttgart Verdrängermaschine
FR2481755A1 (fr) * 1980-04-30 1981-11-06 Poclain Hydraulics Sa Moteur a fluide sous pression muni d'un dispositif de selection de sa vitesse de rotation
US4474104A (en) * 1983-04-11 1984-10-02 Double A Products Co. Control system for variable displacement pumps and motors
DE3313974A1 (de) * 1983-04-18 1984-10-25 Paul Pleiger Maschinenfabrik, 5810 Witten Verfahren und vorrichtung zum steuern von hydromotoren
US4710106A (en) * 1984-11-26 1987-12-01 Nippondenso Co., Ltd. Volume controlling device for variable volume pump
US4768340A (en) * 1987-04-24 1988-09-06 Allied-Signal Inc. Automatic displacement control for variable displacement motor
EP0329860A1 (en) * 1988-02-25 1989-08-30 RIVA CALZONI S.p.A. Apparatus for the feed and the speed and torque control of a hydraulic motor with variable displacement at constant pressure
DE3818105A1 (de) * 1988-05-27 1989-12-07 Pleiger Maschf Paul Vorrichtung zum verstellen des schluckvolumens eines radialkolbenmotors

Also Published As

Publication number Publication date
US5117634A (en) 1992-06-02
DE3910728A1 (de) 1990-10-04
DE59000366D1 (de) 1992-11-26
EP0391097A1 (de) 1990-10-10
DE3910728C2 (enrdf_load_stackoverflow) 1991-06-06
RU2013643C1 (ru) 1994-05-30
DD297486A5 (de) 1992-01-09
CA2012510A1 (en) 1990-10-03

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