DE4302977A1 - Hydraulic plant with pump or motor - generates 180 deg. phase-displaced compensation wave against uneven surface of pressure medium flow - Google Patents

Hydraulic plant with pump or motor - generates 180 deg. phase-displaced compensation wave against uneven surface of pressure medium flow

Info

Publication number
DE4302977A1
DE4302977A1 DE19934302977 DE4302977A DE4302977A1 DE 4302977 A1 DE4302977 A1 DE 4302977A1 DE 19934302977 DE19934302977 DE 19934302977 DE 4302977 A DE4302977 A DE 4302977A DE 4302977 A1 DE4302977 A1 DE 4302977A1
Authority
DE
Germany
Prior art keywords
machine
medium flow
pressure medium
pump
compensator
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.)
Ceased
Application number
DE19934302977
Other languages
German (de)
Inventor
Dieter Dipl Ing Weigle
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to DE19934302977 priority Critical patent/DE4302977A1/en
Publication of DE4302977A1 publication Critical patent/DE4302977A1/en
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/008—Reduction of noise or vibration
    • 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
    • F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
    • F04B11/005—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons
    • F04B11/0075—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation using two or more pumping pistons connected in series
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0042—Systems for the equilibration of forces acting on the machines or pump
    • F04C15/0049—Equalization of pressure pulses
    • 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
    • F04B2205/00—Fluid parameters
    • F04B2205/12—Pressure pulsations before the pump
    • 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
    • F04B2205/00—Fluid parameters
    • F04B2205/13—Pressure pulsations after the pump

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)

Abstract

The hydrostatic engine (10) has a pressure sensor (14) in its intake or discharge section, to measure the amplitude of the uneven surface of the pressure medium flow. The generated signal is processed in a controller (C) with associated intensifier (A). The controller operates a volume compensator (VC) e.g. a piezo compensator, which is located on the high pressure side. The compensator has action against the pressure medium flow, and transmits a compensation wave of the same instantaneous amplitude, which is phase-displaced through 180 deg., against the uneven amplitudes. An additional pressure sensor (15) is located downstream of the volume compensator, to detect any residual unevenness. ADVANTAGE - Provides for noise reduction. Uses simple method for very effective pulsation damping.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Hydraulikanlage nach der Gattung des Hauptanspruchs. In derartigen Hydraulikanlagen werden Geräusche hauptsächlich durch hydrostatische Maschinen erzeugt, da durch deren endliche Zahl von Förderelementen Pulsationen mit entsprechender Ge­ räuschbildung entstehen. Es ist bekannte, in Hydraulikanlagen Pulsa­ tionsdämpfer nach Art von Hydraulikspeichern einzusetzen, die jedoch sehr voluminös, schwer und auch teuer sind.The invention is based on a hydraulic system of the type of the main claim. Noises are generated in such hydraulic systems mainly produced by hydrostatic machines, because of their finite number of conveying elements pulsations with corresponding Ge noise is generated. It is well known in Pulsa hydraulic systems tion damper to use in the manner of hydraulic accumulators, however are very voluminous, heavy and also expensive.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Hydraulikanlage mit den kennzeichnenden Merk­ malen des Hauptanspruchs hat demgegenüber den Vorteil, daß eine sehr gute Pulsationsdämpfung mit einfachsten Mitteln erreicht wird. Die Überlegung geht dahin, der Welligkeit des Druckmittelstroms eine um 180° phasenverschobene Kompensationswelle gleicher Momentanamplitude entgegenzusetzen. Weitere Vorteile der Erfindung ergeben sich aus der Beschreibung, den Unteransprüchen und der Zeichnung. The hydraulic system according to the invention with the characteristic note Painting the main claim has the advantage that a very good pulsation damping is achieved with the simplest of means. The The idea is that the ripple of the pressure medium flow is one 180 ° phase-shifted compensation wave of the same instantaneous amplitude to oppose. Further advantages of the invention result from the description, the subclaims and the drawing.  

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der nachfolgenden Be­ schreibung und Zeichnung näher erläutert. Letztere zeigt in schema­ tischer Darstellung ein Ausführungsbeispiel der Erfindung.An embodiment of the invention is in the following Be spelling and drawing explained in more detail. The latter shows in scheme table representation of an embodiment of the invention.

Beschreibung des ErfindungsbeispielsDescription of the invention example

In der Zeichnung ist mit 10 eine hydrostatische Pumpe bezeich­ net, - es kann sich um eine Zahnradpumpe, eine Flügelpumpe oder eine Kolbenpumpe handeln - die Druckmittel aus einem Behälter 11 ansaugt und dieses in eine Förderleitung 12 verbringt. Die Förderleitung weist eine Krümmung 13 auf und führt von dort zu einem nicht näher dargestellten hydraulischen System. Im Sauganschluß 14 oder in der Förderleitung 12 unmittelbar hinter der Pumpe 10 ist ein Drucksensor 15 angeordnet, welcher die Welligkeit des Druckmittelstroms erfaßt. Das Signal des Drucksensors 15 wird in einem Controller C mit ange­ bautem Verstärker A verarbeitet, der einen hochdynamischen Volu­ men-Compensator VC ansteuert, der in der Förderleitung 12 zwischen der Pumpe 10 und dem Hydrauliksystem angeordnet ist, und zwar vor­ zugsweise im Leitungskrümmer 13 mit Wirkrichtung gegen den Druck­ mittelstrom. Der Volumen-Compensator VC ist zum Beispiel ein Pie­ zo-Volumen-Compensator. Er sendet der Welligkeit des Druckmittel­ stroms eine um 180° phasenverschobene Kompensationswelle gleicher Momentan-Amplitude entgegen, indem er sich bei einem Druckberg zu­ sammenzieht, bei einem Drucktal ausdehnt. Ein zweiter Sensor 16 hin­ ter dem Volumen-Compensator registriert eine eventuell noch ver­ bleibende Restwelligkeit und korrigiert über den Controller C die Arbeit des Volumen-Compensators VC im Sinne höchster Wirksamkeit.In the drawing, 10 is a hydrostatic pump, - it can be a gear pump, a vane pump or a piston pump - sucks the pressure medium from a container 11 and spends it in a delivery line 12 . The delivery line has a bend 13 and leads from there to a hydraulic system, not shown. A pressure sensor 15 , which detects the ripple of the pressure medium flow, is arranged in the suction connection 14 or in the delivery line 12 directly behind the pump 10 . The signal of the pressure sensor 15 is processed in a controller C with a built-in amplifier A, which controls a highly dynamic volume compensator VC, which is arranged in the delivery line 12 between the pump 10 and the hydraulic system, preferably before in the elbow 13 with Direction of action against the pressure medium flow. The volume compensator VC is, for example, a piezo volume compensator. It sends the ripple of the pressure medium flow a 180 ° phase-shifted compensation wave of the same instantaneous amplitude by contracting at a pressure mountain, expanding at a pressure valley. A second sensor 16 behind the volume compensator registers any residual ripple that may still remain and corrects the work of the volume compensator VC via controller C in the sense of maximum effectiveness.

Es sei erwähnt, daß eine derartige Kompensation natürlich nicht nur bei Pumpen zweckmäßig ist, sondern auch bei hydrostatischen Motoren. Es sei auch ausdrücklich nochmals erwähnt, daß nur auf einer Seite der Maschine ein Drucksensor angeordnet ist, d. h. also auf der Nie­ derdruckseite oder auf der Hochdruckseite. Die Zeichnung darf da­ rüber nicht hinwegtäuschen.It should be noted that such compensation is of course not only is useful for pumps, but also for hydrostatic motors. It should also be explicitly mentioned that only on one side a pressure sensor is arranged on the machine, d. H. so on the never on the pressure side or on the high pressure side. The drawing can be there don't hide it.

Claims (6)

1. Hydraulikanlage mit mindestens einer hydrostatischen Maschine (10) (Pumpe oder Motor) und mit Mitteln zur Unterdrückung der von der Maschine durch Pulsation erzeugten Geräusche, dadurch gekenn­ zeichnet, daß im Ein- oder Auslaßbereich der hydrostatischen Ma­ schine (10) ein Drucksensor (14) angeordnet ist, der die Welligkeit des Druckmittelstroms mißt, daß das so erhaltene Signal in einem Controller C mit zugeordnetem Verstärker A verarbeitet wird und der Controller C/A einen Volumen-Compensator VC ansteuert, der auf der Hochdruckseite mit Wirkung gegen den Druckmittelstrom angeordnet ist und der Welligkeit eine um 180° phasenverschobene Kompensationswelle gleicher Momentan-Amplitude entgegensendet.1. Hydraulic system with at least one hydrostatic machine ( 10 ) (pump or motor) and with means for suppressing the noise generated by the machine by pulsation, characterized in that in the inlet or outlet area of the hydrostatic machine ( 10 ) a pressure sensor ( 14 ) is arranged, which measures the ripple of the pressure medium flow, that the signal thus obtained is processed in a controller C with an associated amplifier A and the controller C / A controls a volume compensator VC, which is arranged on the high pressure side with effect against the pressure medium flow and the ripple sends a 180 ° phase-shifted compensation wave of the same instantaneous amplitude. 2. Anlage nach Anspruch 1, dadurch gekennzeichnet, daß der Compen­ sator VC ein Piezo-Volumen-Compensator ist.2. Plant according to claim 1, characterized in that the Compen sator VC is a piezo volume compensator. 3. Anlage nach Anspruch 1 und/oder 2, dadurch gekennzeichnet, daß die hydraulische Maschine (10) eine Pumpe ist und der Volumen­ strom-Compensator VC zwischen dieser und einem von dieser Pumpe be­ aufschlagten Hydrauliksystem angeordnet ist. 3. Plant according to claim 1 and / or 2, characterized in that the hydraulic machine ( 10 ) is a pump and the volume flow compensator VC is arranged between this and a hydraulic system be served by this pump. 4. Anlage nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß der Volumen-Compensator VC mit Wirkrichtung gegen den Druck­ mittelstrom der hydraulischen Maschine in einem Leitungskrümmer der Hydraulikanlage integriert ist.4. Plant according to one of claims 1 to 3, characterized in that the volume compensator VC with direction of action against the pressure medium flow of the hydraulic machine in a pipe bend Hydraulic system is integrated. 5. Anlage nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, daß ein weiterer Drucksensor (15) stromabwärts des Volumen-Compen­ sators VC angebracht ist, der eine eventuell noch verbliebene Rest­ welligkeit erfaßt und das Ausgangssignal des Volumen-Compensators korrigiert.5. Plant according to one of claims 1 to 4, characterized in that a further pressure sensor ( 15 ) is attached downstream of the volume compensator VC, which detects any remaining ripple and corrects the output signal of the volume compensator. 6. Anlage nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß die hydrostatische Maschine eine Zahnradmaschine, eine Kolben­ maschine oder eine Flügelzellenmaschine ist.6. Plant according to one of claims 1 to 5, characterized in that that the hydrostatic machine is a gear machine, a piston machine or a vane machine.
DE19934302977 1993-02-03 1993-02-03 Hydraulic plant with pump or motor - generates 180 deg. phase-displaced compensation wave against uneven surface of pressure medium flow Ceased DE4302977A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
DE19934302977 DE4302977A1 (en) 1993-02-03 1993-02-03 Hydraulic plant with pump or motor - generates 180 deg. phase-displaced compensation wave against uneven surface of pressure medium flow

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19934302977 DE4302977A1 (en) 1993-02-03 1993-02-03 Hydraulic plant with pump or motor - generates 180 deg. phase-displaced compensation wave against uneven surface of pressure medium flow

Publications (1)

Publication Number Publication Date
DE4302977A1 true DE4302977A1 (en) 1994-03-31

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5560205A (en) * 1994-12-21 1996-10-01 Caterpillar Inc. Attenuation of fluid borne noise
DE19918455A1 (en) * 1999-04-23 2000-11-02 Bayerische Motoren Werke Ag Active noise suppression in hydraulic unit of motor vehicle by controlling vibration of actuator to compensate for other sources of vibration
WO2007065640A1 (en) * 2005-12-08 2007-06-14 Airbus Deutschland Gmbh Device for reducing hydraulic-fluid oscillation in a hydraulic system
DE102008019488A1 (en) * 2008-04-17 2009-10-22 Behr Gmbh & Co. Kg Fluiddruckpulsationsdämpfungsvorrichtung
WO2010063661A2 (en) * 2008-12-05 2010-06-10 Siemens Vai Metals Technologies Gmbh & Co Method and device for actively suppressing pressure oscillations in a hydraulic system
WO2010063664A1 (en) * 2008-12-05 2010-06-10 Siemens Vai Metals Technologies Gmbh & Co Method and device for the semi-active reduction of pressure oscillations in a hydraulic system
WO2012000481A3 (en) * 2010-06-29 2012-04-26 Schaeffler Technologies AG & Co. KG Method for carrying out volume compensation in a dual clutch gearbox with hydrostatic engagement system
WO2014086484A2 (en) * 2012-12-07 2014-06-12 Arburg Gmbh + Co. Kg Method for operating a hydraulic device with pump and servomotor, and associated hydraulic device

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3844059A1 (en) * 1988-12-28 1990-08-30 Allweiler Ag DEVICE AND METHOD FOR MOVING FLUID MEDIA

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3844059A1 (en) * 1988-12-28 1990-08-30 Allweiler Ag DEVICE AND METHOD FOR MOVING FLUID MEDIA

Cited By (22)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5560205A (en) * 1994-12-21 1996-10-01 Caterpillar Inc. Attenuation of fluid borne noise
DE19918455A1 (en) * 1999-04-23 2000-11-02 Bayerische Motoren Werke Ag Active noise suppression in hydraulic unit of motor vehicle by controlling vibration of actuator to compensate for other sources of vibration
DE19918455B4 (en) * 1999-04-23 2006-12-07 Bayerische Motoren Werke Ag Method for active noise reduction in hydraulic units
DE102005058547B4 (en) * 2005-12-08 2012-04-12 Airbus Operations Gmbh Device for reducing hydrofluidic vibrations in a hydraulic system
WO2007065640A1 (en) * 2005-12-08 2007-06-14 Airbus Deutschland Gmbh Device for reducing hydraulic-fluid oscillation in a hydraulic system
JP2009518594A (en) * 2005-12-08 2009-05-07 エアバス・ドイチュラント・ゲーエムベーハー Device for reducing hydraulic fluid vibrations in hydraulic systems
CN101326375B (en) * 2005-12-08 2013-03-27 空中客车德国运营有限责任公司 Device for reducing hydraulic-fluid oscillation in a hydraulic system
US8337179B2 (en) 2005-12-08 2012-12-25 Airbus Operations Gmbh Device for reducing hydraulic-fluid oscillation in a hydraulic system
DE102008019488A1 (en) * 2008-04-17 2009-10-22 Behr Gmbh & Co. Kg Fluiddruckpulsationsdämpfungsvorrichtung
EP2116752A1 (en) * 2008-04-17 2009-11-11 Behr GmbH & Co. KG Fluid pressure pulsation attenuation device
WO2010063664A1 (en) * 2008-12-05 2010-06-10 Siemens Vai Metals Technologies Gmbh & Co Method and device for the semi-active reduction of pressure oscillations in a hydraulic system
CN102271832A (en) * 2008-12-05 2011-12-07 西门子Vai金属科技有限责任公司 Method and device for the semi-active reduction of pressure oscillations in a hydraulic system
WO2010063661A3 (en) * 2008-12-05 2010-07-29 Siemens Vai Metals Technologies Gmbh & Co Method and device for actively suppressing pressure oscillations in a hydraulic system
WO2010063661A2 (en) * 2008-12-05 2010-06-10 Siemens Vai Metals Technologies Gmbh & Co Method and device for actively suppressing pressure oscillations in a hydraulic system
CN102256716A (en) * 2008-12-05 2011-11-23 西门子Vai金属科技有限责任公司 Method and device for actively suppressing pressure oscillations in a hydraulic system
CN102256716B (en) * 2008-12-05 2013-11-06 西门子Vai金属科技有限责任公司 Method and device for actively suppressing pressure oscillations in a hydraulic system
RU2526647C2 (en) * 2008-12-05 2014-08-27 Сименс Фаи Металз Текнолоджиз Гмбх Method and device for active suppression of pressure oscillations in hydraulic system
RU2527496C2 (en) * 2008-12-05 2014-09-10 Сименс Фаи Металз Текнолоджиз Гмбх Method and device for semi-active suppression of pressure oscillations in hydraulic system
WO2012000481A3 (en) * 2010-06-29 2012-04-26 Schaeffler Technologies AG & Co. KG Method for carrying out volume compensation in a dual clutch gearbox with hydrostatic engagement system
WO2014086484A2 (en) * 2012-12-07 2014-06-12 Arburg Gmbh + Co. Kg Method for operating a hydraulic device with pump and servomotor, and associated hydraulic device
WO2014086484A3 (en) * 2012-12-07 2014-07-31 Arburg Gmbh + Co. Kg Method for operating a hydraulic device with pump and servomotor, and associated hydraulic device
US9845812B2 (en) 2012-12-07 2017-12-19 Arburg Gmbh + Co Kg Method for operating a hydraulic device with pump and servomotor, and associated hydraulic device

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