WO2013064136A1 - Dispositif de réduction d'une variation de pression dans une conduite remplie de fluide - Google Patents

Dispositif de réduction d'une variation de pression dans une conduite remplie de fluide Download PDF

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Publication number
WO2013064136A1
WO2013064136A1 PCT/DE2012/001042 DE2012001042W WO2013064136A1 WO 2013064136 A1 WO2013064136 A1 WO 2013064136A1 DE 2012001042 W DE2012001042 W DE 2012001042W WO 2013064136 A1 WO2013064136 A1 WO 2013064136A1
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WO
WIPO (PCT)
Prior art keywords
pressure
fluid
piston
line
membrane
Prior art date
Application number
PCT/DE2012/001042
Other languages
German (de)
English (en)
Inventor
Konrad Lentner
Original Assignee
Eads Deutschland 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 Eads Deutschland Gmbh filed Critical Eads Deutschland Gmbh
Publication of WO2013064136A1 publication Critical patent/WO2013064136A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L55/00—Devices or appurtenances for use in, or in connection with, pipes or pipe systems
    • F16L55/04—Devices damping pulsations or vibrations in fluids
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16L—PIPES; JOINTS OR FITTINGS FOR PIPES; SUPPORTS FOR PIPES, CABLES OR PROTECTIVE TUBING; MEANS FOR THERMAL INSULATION IN GENERAL
    • F16L55/00—Devices or appurtenances for use in, or in connection with, pipes or pipe systems
    • F16L55/04—Devices damping pulsations or vibrations in fluids
    • F16L55/041—Devices damping pulsations or vibrations in fluids specially adapted for preventing vibrations

Definitions

  • the present invention relates to hydraulic systems in means of transport.
  • the present invention relates to the reduction of pressure fluctuations in a fluid-filled conduit of a means of transport, in particular of an aircraft.
  • the present invention relates to a device for reducing pressure fluctuation in a fluid-filled conduit, in particular in an aircraft, a hydraulic system and an aircraft.
  • Hydraulic systems are used in means of transport, such as airplanes, to perform a variety of control operations. It may happen that hydraulic lines required for this purpose are distributed or arranged over a large area in the means of transport. Thus, in an aircraft cabin, for example in the area of the side trim between the aircraft envelope and passenger cabin, or else in the overhead area, in the area of the overhead racks, large-volume hydraulic lines can essentially run through the entire aircraft.
  • Such hydraulic pumps can be designed, for example, as axial piston pumps.
  • known hydraulic pumps by virtue of their design, potentially produce, in addition to the required, substantially constant system pressure, also pressure fluctuations, which occur, for example, in the case of pressure fluctuations. as a hydraulic pressure pulsation, modulated or added to the system pressure, can represent.
  • a hydraulic line system for example a large-scale line system, as can be used in an aircraft, vibrations can occur in the line system due to these hydraulic pulsations, which cause additional problems.
  • CONFIRMATION COPY can represent loadings of the system and also, via different transmission paths, such as the connection of hydraulic lines to the aircraft structure, can provide acoustic interference. Such acoustic disturbances may, for example, be perceptible to a passenger in a quiet aircraft environment and reduce their sense of comfort in the aircraft.
  • Resonators usually represent, due to the dimensions of the required wavelengths, as relatively large devices, which also have only a certain, narrow-band use frequency range, since the dimensions of the resonators requires a certain frequency dependence.
  • Absorbers in turn withdraw energy from the hydraulic system, which is undesirable.
  • One aspect of the present invention can thus be seen to provide a preferred, flexible, in particular frequency-flexible possibility for reducing pressure fluctuations in a fluid-filled line, thus reducing hydraulic pulsations in this line and thus reducing acoustic disturbances and mechanical loads on the line system ,
  • a device for reducing pressure fluctuation in a fluid-filled conduit adapted for connection to a fluid conduit, having a supply side and a discharge side.
  • the device has an actively controllable actuator element, which is arranged on the fluid line between the supply side and the discharge side.
  • a first fluid pressure which essentially consists of a first Fluidteiiyak, thus the (constant) system pressure
  • a second Fluidteiiyak which is as the hydraulic pulsation in the hydraulic system, thus representing a pressure fluctuation or as dynamically changing pressure composed.
  • the device according to the invention is intended to compensate the first fluid pressure on the supply side in a substantially constant second fluid pressure on the discharge side.
  • the actuator element for generating a compensation force is controllable, wherein the compensation force compensates the second fluid partial pressure such that the second fluid pressure substantially corresponds to the first fluid partial pressure.
  • the actuator element is intended to substantially equalize the second fluid partial pressure by a suitable second counter-fluid partial pressure.
  • a hydraulic system in particular for an aircraft, which has a device according to the invention for reducing a pressure fluctuation in a fluid-filled line.
  • an aircraft comprising a hydraulic system according to the invention and / or a device according to the invention for reducing pressure fluctuation in a fluid-filled line is provided.
  • the device according to the invention is in this case connected to the hydraulic line in such a way that a line pressure which arrives in the hydraulic line at a supply side of the device and which consists of a line Sense constant system pressure and a hydraulic pulsation or a pulsation pressure can be converted by suitable measures on a discharge side of the device in a substantially constant system pressure.
  • the device can in this case in a section of the hydraulic line, which can also be referred to as a pumping chamber, change the volume of the hydraulic line or the pumping chamber to the effect that the pulsation pressure is compensated.
  • a section of the hydraulic line which can also be referred to as a pumping chamber
  • change the volume of the hydraulic line or the pumping chamber to the effect that the pulsation pressure is compensated.
  • the volume of the pumping chamber may be increased such that the positive pulsation pressure is corrected to zero.
  • the volume in the pumping chamber can be reduced, so that likewise the now present negative pulsation pressure is compensated to zero.
  • a desired or required system pressure is first necessary, as well as information on a currently present pressure in the fluid-filled line system.
  • This line pressure may initially be determined specifically for the device according to the invention, for example via a suitably arranged sensor element, or may be known from other control systems.
  • the required or desired system pressure can also be calculated from a system pressure determined by the sensor element, for example by a simple averaging.
  • the device according to the invention can be used flexibly, since it is not exclusively related to a predetermined system pressure, but rather can determine the constant system pressure itself from a measured dynamic line pressure.
  • a defined, desired system pressure can also be specified.
  • the device according to the invention can also take into account a possible propagation velocity of pressure fluctuations to be compensated which, for example, can be used to compensate delayed pressure fluctuations measured at a sensor element in order to take into account the propagation velocity of the pressure fluctuations in the fluid.
  • a control element may be the active actuator element according to the invention, for example a piezoelectric element which is e.g. is coupled to a piston element, so drive, so that a volume variation of a pumping chamber can be realized.
  • a second sensor element can be used in the discharge area of the hydraulic line in order to verify the compensation of the pulsation pressure. Both sensor signals can be used in the control element for controlling the active actuator element according to the invention. Also, a sensor element in the discharge region can be used as the only sensor element.
  • the device according to the invention may comprise a membrane element having a first side and a second side.
  • the actuator element can in this case be connected to the membrane element, for example, be in contact with it.
  • the actuator element may be connected to the second side of the membrane element, so as to deliver a compensation force to the membrane element.
  • the membrane element can in this case change its shape such that the compensation force is introduced into the fluid line or the required volume variation in the pumping chamber to compensate for the pulsation pressure is realized.
  • the pumping chamber can be arranged on the first side of the membrane element opposite the actuator element and essentially the first partial pressure of the fluid can act.
  • the membrane element can thus be regarded as a laterally fixed piston element.
  • the use of a piston element is also possible, with a laterally mounted membrane element obviating the need for sealing the piston element to its bulb wall.
  • the membrane element may have a mechanically stable configuration, for example a metal element with an exemplary 4 mm wall thickness, and, for example, withstand high pressures of, for example, 200 bar or more.
  • the membrane element has a supporting element on the side of the actuator element.
  • the support element can apply the first fluid part pressure to the second side of the membrane element, while the first fluid pressure acts on the first side of the membrane element.
  • the pulsation pressure since the constant system pressure, thus the first Fluidteildruck, is substantially compensated by the support element.
  • the device or the membrane element is thus designed balanced, so that it is not burdened by a constant line pressure.
  • the first fluid part pressure can thus be applied by using a spring element as a support element on the second side of the membrane element.
  • the spring element should in this case be set up so stiff to provide a support of the membrane element with respect to the first fluid part pressure, but also so flexibly set up that a movement of the membrane element is made possible by the actuator for compensating the second fluid part.
  • the support element has a first and a second side, wherein the first Side of the support element is attached to the membrane element and wherein the second side of the support element is connected to the Fluidieitung, in particular using a transmission element, so that the first fluid pressure acts on the second side of the support element.
  • the transmission element may in this case be designed to be so sluggish and / or lossy, so that essentially only the first fluid part pressure acts on the second side of the support element, thus only the first fluid part pressure on the support element on the membrane element, in particular on its second side is passed.
  • the membrane element can be used over a large pressure application range since only the differential pressure to be compensated can act on the membrane element.
  • the transmission element is designed as a piston element.
  • the piston element in this case has a first side and a second side, wherein the first side of the piston element is connected to the second side of the support element and the second side of the piston element is connected to the Fluidieitung.
  • the first fluid pressure prevailing in the fluid line can be supported by way of the piston element and the support element on the second side of the membrane element.
  • the first fluid pressure part thus the system pressure, can be regarded as a pressure which undergoes substantially only a very low frequency change.
  • the second fluid part pressure, the pulsation pressure be regarded as a pressure having a comparatively high frequency of change.
  • the piston element has high friction or high loss in its connection or sealing to the piston wall, essentially only the first fluid part pressure, but not the second fluid part pressure, is transmitted via the support element to the second side of the membrane element via the piston element passed.
  • the piston element can thus be understood as a low-pass element for pressure fluctuations, which can pass on the low-frequency or non-changing system pressure via the support element to the membrane element, but not the high-frequency Pulsations- pressure, as this would respond too slowly, for example via appropriately trained friction of the piston element, to follow a high-frequency pulsation pressure.
  • the piston element can be designed as a piston element from the group consisting of a circular piston element and a cylinder piston element.
  • the actuator element may be formed as a piezoelectric actuator element.
  • the piezoelectric actuator element can provide required small deflections at comparatively high force.
  • the piezoelectric actuator element may in this case be designed, for example, as a cylindrical stacking actuator and have a cavity in the middle. This results in a favorable ratio of surface to be cooled to heat-generating volume.
  • a suitable cooling can be provided in the interior of the piezoelectric actuator.
  • the device may further comprise at least one sensor element for determining the first fluid pressure and / or the second fluid pressure, as well as a Steuert. Control element for controlling the actuator element.
  • a currently prevailing first fluid pressure can be determined, which is processed in the control or regulating element in order to determine the first fluid part pressure and the second fluid part pressure. Based on the second fluid part pressure, a control of the actuator element can subsequently take place.
  • Fig. 1 is an exemplary illustration of the principle of operation of the present invention
  • FIG. 2 shows a first exemplary embodiment of a device according to the present invention
  • Figs. 3, 4 show a second exemplary embodiment of a device according to the present invention.
  • FIG. 1 shows an exemplary representation of the functional principle of the present invention.
  • FIG. 1 shows fluid line 10 with supply line 4a and discharge line 4b.
  • a first fluid pressure Qi 14a which is composed of the first fluid part pressure Q 16a, the substantially constant system pressure and the second fluid part pressure ⁇ 16b, the hydraulic pulsation or the pulsation pressure.
  • the device 2 according to the present invention is intended here to compensate the first fluid pressure Qi 14a to a second fluid pressure Q2 14b, which should correspond substantially to the first fluid part pressure Q 16a.
  • Pumping chamber 6 is arranged between supply line 4 a and discharge line 4 b, in which actuator element 18 is connected to a piston element 20 or membrane element 20.
  • the second fluid part pressure .DELTA.S. 16b is intended by deflection of Kolbenrelated. Membrane element 20 compensated using the actuator element 18, i. be corrected to zero.
  • Sensor element 12a can in this case determine the first fluid pressure Qi 14a.
  • Control element 22 can determine the first fluid part pressure Q 16a from the dynamically changing first fluid pressure Qi 14a determined by sensor 12a, for example by averaging and from Q1 and Q subsequently the second fluid part pressure ⁇ 16b. Control element 22 can use this information to control the actuator element 18 so that it generates a back pressure or a negative second fluid part pressure ⁇ 16c, which essentially compensates the second fluid part pressure ⁇ 16b to zero.
  • the second fluid pressure Q2 14b becomes substantially equal to the first fluid pressure part Q16a.
  • sensor element 12b can be provided, which essentially can determine the second fluid pressure Q2 14b.
  • the second fluid pressure Q2 also has a pulsation component ⁇ , which can be used to control the control element 22.
  • FIG. 2 shows an exemplary embodiment of the device 2 according to the invention in cross section.
  • Pumping chamber 6 is arranged between supply line 4 a and supply line 4 b, which essentially represents a membrane element 20 arranged in hydraulic line 10 or in an opening of its wall.
  • Membrane element 20 is firmly anchored in the wall of the hydraulic line and thus supported laterally by this.
  • the diaphragm 20 can be moved by the actuator element 18 in a central region perpendicular to the longitudinal direction of the hydraulic line 10.
  • the volume of the pumping chamber 6 can be varied, which essentially corresponds to a pressure reduction or pressure build-up in the region of the pumping chamber 6.
  • a compensation pressure - Aq 16c can be established, which compensates the second fluid idle pressure Aq 16b substantially to zero.
  • the actuator element 18 is exemplified as a piezoelectric, cylindrical stack actuator with a central cavity 38.
  • Actuator element 18 is disposed on the second side 40b of the membrane element 20 and supported on the opposite side by a counter-pressure element 32.
  • the counterpressure element 32 is fastened to the housing 46 of the device 2 according to the invention, in which also the membrane element 20 is accommodated. Thus, the actuator element 18 is clamped between the membrane element 20 and the counter-pressure element 32.
  • a spring element 28 exemplified as a plate spring, mounted with its first side 42a.
  • the second side 42 b of the support element 28 is arranged on a piston element 24.
  • the piston element has the connection to the support element 28 on its first side 44a.
  • On The second side 44b of the piston element 24 essentially has the effect of the first fluid component pressure Q 16a and the second fluid pressure Q 2 14b, respectively. At least on the section of the cylinder element 24 shown on the left in FIG. 2, the first fluid pressure Qi 14a would first load by means of the connecting line 30.
  • the friction-afflicted seal 26 thus represents a kind of low-pass element, which on the one hand pass the constant line pressure Q 16a via support member 28 to membrane 20, but so lossy or sluggish reacts, so that the variable second Fluidteildruck ⁇ 16b is not disclosed.
  • actuator element 18a may be made as small as possible, for example for reasons of cost or space, so that while it can generate the required dynamic pulses for compensating the second fluid part pressure ⁇ 16b, it is not exposed to the static, first fluid part pressure Q 16a. which he might not be able to withstand. This support of the static pressure load is described again below.
  • actuator element 18 and pump chamber 6 may possibly not be permanently sealed due to the low mechanical stroke with possibly high pressure and high operating frequency due to commonly available sealing systems in combination with a piston, in particular due to the stiction of such a piston with adequately sized sealing systems For example, if the line pressure in the fluid id would correspond to 200 bar or so, and consequent significant wear on a potential piston sealing system.
  • the transmission between the actuator element 18 and the hydraulic medium in the hydraulic line 10 therefore takes place according to the invention and in FIG. 2 by way of example through a membrane element 20, for example a steel membrane, which is designed or arranged such that its inherent rigidity is an order of magnitude less than that of the actuator element 18th
  • the support required to protect the membrane element 20 and the actuator element 18 is provided by a support element 28, exemplified as a plate spring. It should also be noted that the dynamic stiffness of the support element 28 and the disc spring should be significantly lower than that of the actuator element 18, for example, the piezoelectric Stapelak- tuators in order to reduce the required additional forces to a minimum. In this case, the inherent property of a degressive characteristic of a diaphragm spring can be used.
  • the sealing system 26 of the piston element 24 should in this case be subject to high friction in order to prevent, in combination with a possibly high mass of the piston element 24, coupling of the pulsation ⁇ 16b to be eliminated via the diaphragm spring.
  • the coupling of the piston member 24 on the calm side of the flow, thus on the discharge side 4b, is preferable.
  • the piston can, as shown in Figure 2, be designed as an annular piston which is connected directly to the hydraulic line system 10.
  • the device 2 is designed as a closed, pressure-resistant system, in which the housing wall 46 shown in FIG. 2 is closed completely and in particular using the counterpressure element 32 with respect to the hydraulic line 10.
  • an element of the device for example spring element 28, piston element 24 or actuator element 18, is damaged, e.g. breaks down
  • the inventive device with respect to the opening in the hydraulic line 10, as a closed system, so that the operation of the hydraulic line 10 is not affected.
  • the device 2 according to the invention has a fail-safe behavior even in the case of destruction of the membrane element 28, only the required compensation of the second fluid part pressure 16b can no longer be realized in this case.
  • Membrane element 20 can exemplarily have a thickness of 4 mm and in this case provide a deformation in the range of 10-20 ⁇ m.
  • actuator 18, implemented as a piezoelectric actuator element may, for example, have a diameter of 25 mm at a height of 50 mm up to a diameter of 42 mm or more at a height of 100 mm.
  • Supporting element 28 may have a diameter of 200 mm as a plate spring by way of example.
  • the active area of membrane element 20 may exemplarily have a diameter of 100 mm.
  • Possible line pressures of the hydraulic system 1 are in the embodiment according to the invention with steel membrane at up to 200 bar or more.
  • FIGS. 3 and 4 a second exemplary embodiment of the present invention is illustrated.
  • piston element 24 should not be designed as an annular piston element, this may also be formed by a ring element 34 and a plurality of individual piston elements 24.
  • a ring line 36 is provided in connection line 30, which connects the pressure chambers on the second side 44b thereof with the hydraulic line 10, so that the first 14a or second fluid pressure 14b rests on the second side 44b of the piston elements 24.
  • ring member 34 is provided to connect a trained as a plate spring support member 28 to discrete piston elements 24 ring member 34 .
  • ring member 34 serves essentially the power transmission between the piston elements 24 and support member 28th
  • a seal and vibration isolation with respect to the second fluid part pressure Aq 16b is provided by the individual piston elements 24.
  • the central membrane element 20 connected to the actuator element 18 is arranged centrally in FIG. 3.
  • the support element 32 is not shown separately in FIG. 3, but is connected to the housing 46 according to FIG. Device 2 can in this case be designed as a component, which is placed on a suitable opening in a hydraulic line 10 and this concludes suitably for providing the functionality according to the invention.
  • a hydraulic line 10 may, for example, have a standardized opening, which may initially be closed with a clean cover. In the event that the pressure fluctuations occurring in the hydraulic line 10 are to be compensated, such a cover can be easily removed from a hydraulic line 10 and the device 2 according to the invention can be placed.
  • control element 22 may for example be installed directly on the device 2 according to the invention in order to provide the control technology method for compensation of the pulsation pressure, which essentially requires only information of the sensor elements 12a, 12b.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Pipe Accessories (AREA)

Abstract

La présente invention concerne la technique hydraulique, en particulier la compensation de variations de pression dans un système hydraulique (10). Le dispositif (2) selon l'invention utilise un élément d'actionnement (18) pouvant être commandé activement et compensant une première pression de fluide (14a) dans une conduite de fluide (10), ladite pression présentant en particulier une pression partielle (16b) dynamiquement variable, de telle sorte que sensiblement la pression de conduite constante (16a) reste dans la conduite de fluide (10) après son passage à travers le dispositif (2) selon l'invention. Le dispositif (2) est équilibré de sorte qu'il ne soit pas sollicité par une pression de conduite constante (16a).
PCT/DE2012/001042 2011-11-04 2012-10-29 Dispositif de réduction d'une variation de pression dans une conduite remplie de fluide WO2013064136A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201110117620 DE102011117620A1 (de) 2011-11-04 2011-11-04 Vorrichtung zur Reduzierung einer Druckschwankung in einer fluidgefüllten Leitung
DE102011117620.2 2011-11-04

Publications (1)

Publication Number Publication Date
WO2013064136A1 true WO2013064136A1 (fr) 2013-05-10

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PCT/DE2012/001042 WO2013064136A1 (fr) 2011-11-04 2012-10-29 Dispositif de réduction d'une variation de pression dans une conduite remplie de fluide

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WO (1) WO2013064136A1 (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020203660A1 (de) 2020-03-20 2021-09-23 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung eingetragener Verein Vorrichtung zur Beeinflussung, insbesondere Reduktion, von Schwingungen in einem Fluidsystem und Verfahren zur Beeinflussung, insbesondere Reduktion, von Schwingungen in einem Fluidsystem
CN113551906B (zh) * 2021-07-30 2023-11-28 博格华纳汽车零部件(北京)有限公司 液压驱动系统压力波动测试装置及方法

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3023591A (en) * 1958-09-08 1962-03-06 Alco Valve Co Rate of flow control system for refrigeration
US5526690A (en) * 1995-05-17 1996-06-18 The United States Of America As Represented By The Secretary Of The Navy Circumferential actuator for piping system
EP0971164A2 (fr) * 1999-09-06 2000-01-12 Dobson Industries Corp. Dispositif de réduction de pulsations de pression dans des conduits hydrauliques
EP1298379A1 (fr) * 2001-09-28 2003-04-02 Robert Bosch Gmbh Dispositif pour amortir les pulsations de pression dans un système à fluide, en particulier dans un système à carburant d'un moteur à combustion, et système à carburant

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3023591A (en) * 1958-09-08 1962-03-06 Alco Valve Co Rate of flow control system for refrigeration
US5526690A (en) * 1995-05-17 1996-06-18 The United States Of America As Represented By The Secretary Of The Navy Circumferential actuator for piping system
EP0971164A2 (fr) * 1999-09-06 2000-01-12 Dobson Industries Corp. Dispositif de réduction de pulsations de pression dans des conduits hydrauliques
EP1298379A1 (fr) * 2001-09-28 2003-04-02 Robert Bosch Gmbh Dispositif pour amortir les pulsations de pression dans un système à fluide, en particulier dans un système à carburant d'un moteur à combustion, et système à carburant

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