EP0076876A1 - Dispositif avec une pompe à palettes pour des capacités réglées du débit - Google Patents

Dispositif avec une pompe à palettes pour des capacités réglées du débit Download PDF

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Publication number
EP0076876A1
EP0076876A1 EP81108308A EP81108308A EP0076876A1 EP 0076876 A1 EP0076876 A1 EP 0076876A1 EP 81108308 A EP81108308 A EP 81108308A EP 81108308 A EP81108308 A EP 81108308A EP 0076876 A1 EP0076876 A1 EP 0076876A1
Authority
EP
European Patent Office
Prior art keywords
comparator
arrangement according
pump
pressure
setpoint
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.)
Withdrawn
Application number
EP81108308A
Other languages
German (de)
English (en)
Inventor
Walter Wimmer
Heinz Krüger
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.)
Sperry Vickers Zweigniederlassung Der Sperry GmbH
Original Assignee
Sperry Vickers Zweigniederlassung Der Sperry 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
Application filed by Sperry Vickers Zweigniederlassung Der Sperry GmbH filed Critical Sperry Vickers Zweigniederlassung Der Sperry GmbH
Priority to EP81108308A priority Critical patent/EP0076876A1/fr
Publication of EP0076876A1 publication Critical patent/EP0076876A1/fr
Withdrawn legal-status Critical Current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
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
    • 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
    • F04B49/06—Control using electricity

Definitions

  • the power control of hydraulic pumps is already known and serves to limit the maximum drive power consumption and thus to avoid overloading the drive motor.
  • the output control reduces the flow rate corresponding to a hyperbola with increasing pressure of the hydraulic fluid.
  • the ideal hyperbole could only be approximated by a characteristic curve which results from individual pieces of straight lines corresponding to the force path lines of spring combinations.
  • Another disadvantage of the previous power controllers is the fact that it is difficult to switch from the power once set to another power. Furthermore, it is not possible to cut the pressure when a certain delivery rate is reached.
  • the invention has for its object to provide an arrangement with which it is easily possible to set or adjust the desired output, to improve the quality of the control, in particular in the case of rapid pressure changes, and, if appropriate, the control range within permissible limits of the flow rate and to maintain the delivery pressure.
  • a vane pump 1 has an outer housing with main housing parts 2, 3, which are screwed together in a pressure-tight manner (FIGS. 5, 6).
  • the housing 2, 3 has an interior space 4 which is sufficiently wide to accommodate a race 5 and to move it eccentrically to a rotor 6.
  • the rotor 6 is rotatably connected to a shaft 6a which is mounted in the housing 2, 3.
  • the race 5 has a circular cylindrical interior 6a (FIG. 4) within which the rotor 6 and vanes 7 guided in the rotor are arranged.
  • the race 5 is supported by two opposing pistons 8, 9 (FIG. 1) and a pendulum support 10 (FIGS. 4, 5, 6) which are guided radially to the race 5 in cylindrical bores of the main housing part 2.
  • the main housing part 2 (Fig. 6) has an inlet channel 14 and an outlet channel 15, which are passed in the axial direction of the rotor 6 through pressure plates 16, 17 and open into a suction area 18 and a pressure area 19, respectively, between the race 5, rotor 6 and the wings 7 and are sealed in the axial direction by the pressure plates 16, 17 and further pressure plates 20, 21 (FIG. 5).
  • the pressure plate 20 has a bore 20a, which leads to a pressure cushion space 22, the active surface (parallel to the sectional area in FIG. 4) is larger than the area of the printing area 19.
  • the displacement of the race 5 takes place with the aid of the pistons 8 and 9.
  • At least the piston 8 has a spring 23 (FIG. 4) which holds it in contact with the race 5 and attempts to shift it to the right in FIG. 4 .
  • the pump forces try to move the race 5 to its central position (zero eccentricity).
  • the eccentricity of the race 5 to the rotor 6 can be changed.
  • the delivery flow of the pump changes depending on the sine of the eccentricity and thus on the position of the pistons 8 and 9.
  • a compensator 30 This contains in a housing 31, 32 at least one spring 33 and a slide piston 34, which act as a pressure compensator for the pump pressure which is supplied via channels 25, 35. Corresponding channels 36, 37, 38 either supply or discharge hydraulic fluid to space 8a. If the delivery pressure rises above the limit set by the spring 33, the space 8a is briefly connected to the unpressurized channel 36 and thus the filling quantity in the space 8a behind the piston 8 is reduced, so that the eccentricity of the race 5 and the delivery rate of the pump decrease accordingly decreases accordingly.
  • An electrical displacement-voltage converter 40 serves as the flow meter of the pump.
  • Such displacement-voltage converters 40 are known per se and are available on the market (for example from ETO, Unteruhldingen / Bodensee, Federal Republic of Germany).
  • the displacement-to-voltage converter 40 is connected to the piston 9 with a stylus 41.
  • the position of the piston 9 (as well as that of the piston 8) is a measure of the eccentricity of the race 5.
  • the displacement-to-voltage converter 40 inputs electrical signal from which the recorded Path (the eccentricity of the race 5) corresponds, that is proportional to the hydraulic flow delivered.
  • An electrically adjustable pressure relief valve 45 (FIGS. 1 and 7), which acts as a pilot valve, is attached to the compensator housing 31, the space 46 of which is in hydraulic connection with the delivery line 15 of the pump 1 or the high pressure line 35 in the compensator.
  • a valve cone 47 closes the space 46 and is under the pressure of a valve spring 48, the spring abutment 49 of which is axially adjustable.
  • an electromagnet 50 is used, the armature 51 of which is connected to the spring abutment 49 via a rod 52.
  • the rod 52 carries a plate 53, which cooperates with a second displacement-voltage converter 55, which serves as a pressure limiter.
  • the axial position of the armature 51 and the rod 52 determine the force of the valve spring 48 and thus the response pressure of the pressure relief valve 45.
  • the second travel-voltage converter 55 emits an electrical signal via the response pressure of the pressure relief valve 45 that is set in each case.
  • the output signals of the electrical converters 40 and 55 are fed to a control circuit 60 (FIG. 1), which compares the offered values with a target value and emits an electrical current as a manipulated variable to the electromagnet 50 of the pressure relief valve 45, whereby its response limit is continuously set .
  • the control circuit 60 is constructed so that lines of constant power, e.g. 61, 62, 63 (FIG. 2) can be driven. But it is also possible that the control circuit also sets limits for a maximum pressure 64 and / or a maximum delivery rate 65. 3 shows such a control circuit.
  • a multiplier circuit 70 has two inputs 71, 72 which are connected to the electrical converters 40 and 55, respectively.
  • the multiplier circuit 70 multiplies the input variables on the lines 71 and 72 with one another and bil det on the output line 73 an electrical signal which corresponds to the instantaneous power of the pump 1.
  • a power specification signal is formed at a potentiometer 74 and fed to a setpoint value comparison circuit 80 via a line 75.
  • the result of the comparison is fed to an output line 81 either directly or with the addition of further comparators to a power amplifier 90 which supplies a corresponding current as a manipulated variable via line 91 to the electromagnet 50, so that the appropriate response value of the pressure relief valve 45 is set.
  • the electrical converter 55 is connected via a line 82 to the input side of a position control comparator 83, to which the signal on line 81 is also fed. If no adjustable limitation of the maximum pressure and the maximum flow rate (corresponding to lines 64 and 65 in FIG. 2) is desired by the control circuit 60 ′, the line 84 is connected to the power amplifier 90 on the input side. 3, however, the selectable setting of the maximum delivery pressure and flow is provided and for this purpose there is a maximum flow limiter comparator 85 with setpoint specification potentiometer 86 and a pressure cut-off comparator 87 with pressure limiter setpoint potentiometer 88 provided.
  • the pressure cut-off comparator 87 compares the signals of the comparators 83 and 85 and the potentiometer 88 fed to it on the input side and supplies the result of the comparison to the power amplifier 90 on an output line 89. In this way it is possible to run the pump within the performance field, as this is delimited by lines 63, 64, 65 in FIG. 2.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP81108308A 1981-10-14 1981-10-14 Dispositif avec une pompe à palettes pour des capacités réglées du débit Withdrawn EP0076876A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP81108308A EP0076876A1 (fr) 1981-10-14 1981-10-14 Dispositif avec une pompe à palettes pour des capacités réglées du débit

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP81108308A EP0076876A1 (fr) 1981-10-14 1981-10-14 Dispositif avec une pompe à palettes pour des capacités réglées du débit

Publications (1)

Publication Number Publication Date
EP0076876A1 true EP0076876A1 (fr) 1983-04-20

Family

ID=8187957

Family Applications (1)

Application Number Title Priority Date Filing Date
EP81108308A Withdrawn EP0076876A1 (fr) 1981-10-14 1981-10-14 Dispositif avec une pompe à palettes pour des capacités réglées du débit

Country Status (1)

Country Link
EP (1) EP0076876A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4801247A (en) * 1985-09-02 1989-01-31 Yuken Kogyo Kabushiki Kaisha Variable displacement piston pump
DE3733396A1 (de) * 1987-10-02 1989-04-13 Rexroth Mannesmann Gmbh Elektrische pumpenregelung fuer die foerderstrom- und druckregelung an einem verbraucher
DE4102087A1 (de) * 1991-01-24 1992-07-30 Rexroth Mannesmann Gmbh Schaltungsanordnung zur druckregelung in einem hydraulischen drucksystem
WO1994000691A1 (fr) * 1992-06-22 1994-01-06 Microhydraulics Inc. Pompe a piston radial
EP0646724A1 (fr) * 1993-10-05 1995-04-05 Shin Caterpillar Mitsubishi Ltd. Méthode et dispositif pour commander des systèmes hydrauliques d'un engin de construction

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2969646A (en) * 1957-01-11 1961-01-31 Racine Hydraulics & Machinery Variable volume pump hydraulic transmission
DE1528434A1 (de) * 1965-07-29 1969-09-25 Hymate Ges Fuer Hydr Automatik Hydraulische Reversiersteuerung mit Leistungsreglern
FR2129570A5 (fr) * 1971-03-10 1972-10-27 Bosch
DD98979A1 (fr) * 1972-04-12 1973-07-12
US3924972A (en) * 1974-10-29 1975-12-09 Vilter Manufacturing Corp Control means for a variable capacity rotary screw compressor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2969646A (en) * 1957-01-11 1961-01-31 Racine Hydraulics & Machinery Variable volume pump hydraulic transmission
DE1528434A1 (de) * 1965-07-29 1969-09-25 Hymate Ges Fuer Hydr Automatik Hydraulische Reversiersteuerung mit Leistungsreglern
FR2129570A5 (fr) * 1971-03-10 1972-10-27 Bosch
DD98979A1 (fr) * 1972-04-12 1973-07-12
US3924972A (en) * 1974-10-29 1975-12-09 Vilter Manufacturing Corp Control means for a variable capacity rotary screw compressor

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4801247A (en) * 1985-09-02 1989-01-31 Yuken Kogyo Kabushiki Kaisha Variable displacement piston pump
DE3733396A1 (de) * 1987-10-02 1989-04-13 Rexroth Mannesmann Gmbh Elektrische pumpenregelung fuer die foerderstrom- und druckregelung an einem verbraucher
DE3733396C2 (de) * 1987-10-02 1998-12-17 Rexroth Mannesmann Gmbh Elektrische Pumpenregelung für die Förderstrom- und Druckregelung an einem Verbraucher
DE4102087A1 (de) * 1991-01-24 1992-07-30 Rexroth Mannesmann Gmbh Schaltungsanordnung zur druckregelung in einem hydraulischen drucksystem
WO1994000691A1 (fr) * 1992-06-22 1994-01-06 Microhydraulics Inc. Pompe a piston radial
EP0646724A1 (fr) * 1993-10-05 1995-04-05 Shin Caterpillar Mitsubishi Ltd. Méthode et dispositif pour commander des systèmes hydrauliques d'un engin de construction
US5540554A (en) * 1993-10-05 1996-07-30 Shin Caterpillar Mitsubishi Ltd. Method and apparatus for controlling hydraulic systems of construction equipment

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

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Effective date: 19811023

AK Designated contracting states

Designated state(s): DE FR GB IT

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

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18W Application withdrawn

Withdrawal date: 19860326

RIN1 Information on inventor provided before grant (corrected)

Inventor name: KRUEGER, HEINZ

Inventor name: WIMMER, WALTER