EP0356780B1 - Réservoir pour un circuit de fluide de pression, spécialement pour un circuit hydraulique d'avions - Google Patents

Réservoir pour un circuit de fluide de pression, spécialement pour un circuit hydraulique d'avions Download PDF

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Publication number
EP0356780B1
EP0356780B1 EP89114794A EP89114794A EP0356780B1 EP 0356780 B1 EP0356780 B1 EP 0356780B1 EP 89114794 A EP89114794 A EP 89114794A EP 89114794 A EP89114794 A EP 89114794A EP 0356780 B1 EP0356780 B1 EP 0356780B1
Authority
EP
European Patent Office
Prior art keywords
pressure
partial
piston
rod
reservoir
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
EP89114794A
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German (de)
English (en)
Other versions
EP0356780A3 (fr
EP0356780A2 (fr
Inventor
Joachim Baier
Walter Peterknecht
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.)
ASG Luftfahrttechnik und Sensorik GmbH
Original Assignee
AEG Sensorsysteme 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 AEG Sensorsysteme GmbH filed Critical AEG Sensorsysteme GmbH
Publication of EP0356780A2 publication Critical patent/EP0356780A2/fr
Publication of EP0356780A3 publication Critical patent/EP0356780A3/fr
Application granted granted Critical
Publication of EP0356780B1 publication Critical patent/EP0356780B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/26—Supply reservoir or sump assemblies
    • F15B1/265—Supply reservoir or sump assemblies with pressurised main reservoir

Definitions

  • the invention relates to a reservoir for a pressure medium circuit with a first and a second accumulator piston, which seal a first pressure chamber and second pressure chamber, the effective area of the first accumulator piston being considerably smaller than the area of the second accumulator piston effective against a second pressure chamber. and the first pressure prevailing in the first pressure chamber is very much higher than the second pressure in the second pressure chamber, and wherein the first, high-pressure accumulator piston loads the second accumulator piston via a piston rod in the direction of compression of the pressure medium in the second pressure chamber.
  • a reservoir is used for this purpose, in which a high-pressure chamber for storing a high pressure, which is pumped and made available to the consumer, and a low-pressure chamber, in which the relaxed pressure medium is collected, are provided.
  • a reservoir is shown for example in DE-A-19 26 410.
  • DE-A-18 04 037 is concerned with a partial problem in the construction of such a reservoir.
  • a large low-pressure chamber also requires a large storage volume.
  • Such a low-pressure chamber is usually kept under pressure by means of a second storage piston, which is connected via a piston rod to a high-pressure piston controlled by high pressure. Since the piston rod must be able to reach through the entire low-pressure space, it is very long. On the other hand, only a limited space is available for such a reservoir in mobile vehicles, in particular in aircraft.
  • the invention has for its object to develop a reservoir of the type described above so that it is constructed as space-saving as possible.
  • the piston rod consists of at least two telescopically displaceable partial rods, which are designed so that they enclose a sealed intermediate space between them, which communicates with the first pressure chamber and is limited by brackets of the partial rods acting as intermediate pistons is.
  • the invention therefore consists in making the piston rod connecting the two storage pistons interconnectable, so that their length can be adapted to the respective pressure requirements.
  • the combination of measures from claim 3 caused that the pressure medium located in the low-pressure chamber is drawn by the force of the high pressure in the first pressure chamber onto the first accumulator piston towards the first pressure chamber, so that the second pressure chamber lies between the second accumulator piston and the first pressure chamber.
  • the force exerted by the high pressure is thus used not only to change the position of the part of the piston rod adjoining the first piston, but also to change the position of the two part rods relative to one another.
  • the intermediate space is thus designed as a further high-pressure space, which pushes the two partial rods into one another and thus shortens the piston rod in the desired manner. Which of the partial rods first changes their position depending on the applied pressures depends on the geometric dimensions of the effective pressure surfaces on the first storage piston and on the piston surfaces of the intermediate space, which are formed by the sealingly guided brackets.
  • a feature combination according to claim 5 is recommended in a further development of the invention.
  • the interior of the sleeve-shaped partial rods to be moved into one another is also used to store the low pressure medium.
  • the space above the first partial rod can also be used as a low-pressure space if the partial rods are in a suitable position.
  • the first partial piston rod only begins its movement with respect to the housing when the second partial piston rod has moved into the interior of the first partial piston rod.
  • a combination of features according to claim 7 is recommended for this purpose. According to these features, the position of the first partial piston rod remains unchanged due to the high pressure until the second piston rod that is moving upward has reached its end position. If the second part of the rod is attached to the first part, they form a one-piece part in which the space formed by the two parts can no longer develop dynamic forces and thus forms a closed, no longer expandable space.
  • An expedient embodiment of a stop for the second partial piston rod on the first Partial piston rod describes a combination of features according to claim 8.
  • FIG. 1 shows a reservoir 1 with a first storage piston 2 and a second storage piston 3.
  • the housing of the reservoir 1 is divided into a first pressure chamber 4 and a second pressure chamber 5.
  • the two storage pistons 2 and 3 are connected to one another via a piston rod 6.
  • the pressure chamber 7, which adjoins the second pressure chamber 5 downward in FIG. 1 and lies below the second accumulator piston 3, is connected to the ambient pressure via an opening 8.
  • the space 9 above the first accumulator piston 2 in the housing of the reservoir 1 is connected to the second pressure chamber via a through-hole running along the piston rod 6, so that essentially the same pressure prevails in the spaces 5 and 9.
  • the first pressure chamber 4 used to store the high pressure is surrounded by the two low-pressure chambers 5 and 9, so that the pressure medium leaving the first pressure chamber 4 in the event of a faulty seal either enters the chamber 5 or 9 and thus continues for the pressure medium circuit is available.
  • a hydraulic oil is used as the pressure medium so that it cannot be lost in the event of a leak.
  • a high-pressure pump 10 conveys from the second pressure chamber 5 into the pump chamber and presses the compressed pressure medium (double arrow) to a consumer 11.
  • the pressure medium relaxes within the consumer and is returned to the second pressure chamber 5 in the relaxed state (simple arrow).
  • the excess, highly compressed pressure medium reaches the high-pressure chamber 4 and is stored there and at the same time used to compress the pressure medium in the second pressure chamber. This is done by the fact that the first accumulator piston 2 takes the second accumulator piston 3 in FIG. 1 upward via the piston rod 6 and thus brings the hydraulic oil in the second pressure chamber 5 to the necessary low pressure that the pump 10 needs to achieve the necessary pumping capacity.
  • the ratio of the effective areas of the first and second accumulator pistons is reversed to the pressure prevailing in the first and second pressure chambers. If the high pressure (two arrows) increases too high, this pressure is reduced via a pressure relief valve V and the excess pressure medium is returned to the second pressure chamber.
  • FIG. 2 shows in section a schematic illustration of a reservoir according to the invention, with assemblies of the same value as in FIG. 1 being given the same reference numerals.
  • the reservoir is rotationally symmetrical, but circumferential edges for reasons of greater clarity were omitted.
  • the housing of the reservoir 1 consists essentially of a smaller first cylinder 20 and a larger two th cylinder 19.
  • the second working piston 3 divides the second cylinder 19 into an ambient pressure chamber 7, which is connected via an opening 8 to the ambient pressure and into a low pressure chamber 5, in which the pressure medium coming back from the consumer 11 is stored.
  • the second pressure chamber 5 serving as a low-pressure chamber is connected to the chamber 19 via a connecting opening 21, so that there is also low pressure in the chamber 9.
  • the low-pressure medium preferably hydraulic oil, enters the low-pressure chamber 5 via the low-pressure inlet 22 and is supplied via a second, not shown.
  • Low pressure outlet led to the input of the pump 10. Via a high-pressure inlet 23, high-pressure pressure medium reaches the first pressure chamber 4 from the outlet of the pump.
  • the construction of the piston rod (6 in FIG. 1) is now essential for the invention, which is composed of two sleeve-shaped partial rods 15, 16, which can be telescoped into one another.
  • the first partial rod 15 carries the first accumulator piston 12 at its upper end in FIG. 2, while the second partial rod 16 is connected in one piece to the second accumulator piston 3 at its lower end in FIG.
  • Both the first partial rod 15 and the second partial rod 16 each have a circumferential bracket 14 or 13, which engage one behind the other when the partial rods are pulled apart and thus form a stop which prevents the two partial rods from being pulled apart further.
  • the brackets 13 and 14 are simultaneously sealingly guided on the lateral surfaces of the other partial rod, the console 13 slidingly sealingly on the inner lateral surface of the first partial rod 15 and the console 14 on the outer lateral surface of the second partial rod 16.
  • a sealed intermediate space 24 is created, in which the two brackets 13, 14 act as an intermediate piston.
  • the intermediate space 24 is connected to the first pressure space 4 via an access channel 17, so that there is also high pressure there and this intermediate space can be regarded as part of the first pressure space. This is indicated with a corresponding reference number.
  • the lower end of the first partial rod 15 is supported on the side walls of the second cylinder 19 by a support 25 which is permeable to pressure medium.
  • the ratio is effective areas F1 and F2 are decisive.
  • the effective area F1 is as large as the area effective for high pressure F2, ie the two ring areas F1 and F2 have the same area, whereby ring F1 with the smaller diameter must naturally be wider than the ring F2 with the larger diameter. This ensures that the first partial rod 15 remains in its position as long as no other forces act on it than the high pressure. If the pressure in the pressure chamber 4 is as high as in the intermediate space 24 and no other forces act on the first partial rod 15, this does not change its position.
  • brackets 12 and 14 exposed to the low pressure in the pressure chambers 5 and 9 also have the same effective area F5 and F6 with respect to the low pressure and that the access channel 17 likewise does not cause the first partial rod 15 to move because of the same area contribute.
  • the movement of the piston rod 15, 16 is therefore only caused by the movement of the second partial rod 16, for example by raising this second partial rod within the first partial rod 15 or by the second partial rod 16 after it has struck the console 14 with the second working piston 3, which takes the first partial rod 15 on their way up.
  • the friction forces of the seal on the partial rods are neglected or take into account that the friction forces of the seals with the larger circumference, which act on the outer surface of the first partial rod 15, are greater than the friction forces of the brackets 13 and 14.
  • FIG. 3 A possible sequence of movements within the reservoir according to the invention will be explained below with reference to FIGS. 3 to 6, in which case it is assumed in FIG. 3 that the reservoir in its low-pressure chamber 5 is completely filled with hydraulic oil while there is still no high pressure on the high-pressure inlet . 3 to 6, reference numerals have been omitted which can be found in FIG. 2.
  • the second accumulator piston 3 is in its lowermost position, so that it has its maximum low-pressure space. If pressure medium under high pressure is now introduced into the high-pressure inlet 23, the first sub-piston 15 remains stationary and the second sub-piston 16 begins to start up within the first sub-piston 15. If a force equalization between the high pressure pressing on the surface F1 and the low pressure acting on the accumulator piston 3 is already achieved during this path, the piston 16 remains at the relevant point within the piston 15, while the piston 15 in Fig. 3 does not change its position.
  • FIG. 4 shows the position of the second partial rod in which it strikes against the lower part of the first partial rod 15 by means of the second accumulator piston 3.
  • the accumulator piston pulls the second partial rod 16 down a suitable distance again, as can be seen, for example, in FIG. 2. This continues until finally the lower edge of the bracket 13 engages the upper edge of the bracket 14 and the second partial bar 16 takes the first partial bar 15 downward.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Actuator (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Braking Arrangements (AREA)

Claims (12)

  1. Réservoir pour un circuit de fluide de pression avec un premier (12) et un second pistons d'accumulation (3) qui rendent étanche une première chambre de pression (4) resp. une seconde chambre de pression (5), la surface active (F2) du premier piston d'accumulation (12) étant considérablement plus petite que la surface active du second piston d'accumulation (3), par rapport à une seconde chambre de pression (5) et la première pression dominante dans la première chambre de pression (4) étant bien plus élevée que la seconde pression dans la seconde chambre de pression (5), et le premier piston d'accumulation (12) soumis à la haute pression chargeant le second piston d'accumulation (3) par l'intermédiaire d'une tige de piston (15, 16) vers une compression du fluide de pression dans la seconde chambre de pression (5),
    caractérisé en ce que
    la tige de piston (15, 16) se compose d'au moins deux parties de tige coulissantes (15, 16) l'une dans l'autre de manière télescopique qui sont conçues de sorte qu'elles enferment entre elles une chambre intermédiaire (24) étanche qui est reliée à la première chambre de pression (4) et est limitée par des consoles (13, 14) des parties de tiges (16, 15), ces consoles agissant comme pistons intermédiaires.
  2. Réservoir selon la revendication 1, caractérisé en ce que les parties de tige (15, 16) disposent de butées agissant l'une sur l'autre et/ou en liaison avec l'enveloppe de réservoir environnante qui limitent la plus grande longueur (fig. 3) et/ou la plus petite longueur (fig. 6) à l'état sorti et/ou rentré de la tige de piston (15, 16).
  3. Réservoir selon la revendication 2, caractérisé en ce que la tige de piston (15, 16) est sollicitée à la traction et les parties de tiges de piston (15 resp. 16) disposent de consoles (14, 13) annulaires, qui limitent leur état sorti, qui s'engagent l'une derrière l'autre et qui constituent des butées.
  4. Réservoir selon la revendication 2 ou 3, caractérisé en ce que chaque console (14, 13) des parties de tiges (15 resp. 16) est guidée de manière étanche le long de la surface d'enveloppe interne resp. externe de l'autre partie de tige de piston en forme de manchon et que la chambre intermédiaire (24) se trouvant entre les consoles (13, 14) est reliée, par un canal (17), à la première chambre de pression (4) amenant la haute pression.
  5. Réservoir selon la revendication 4, caractérisé en ce que les chambres internes des parties de tige sorties en forme de manchon s'enchaînent les unes dans les autres et sont reliées à la seconde chambre de pression contenant la basse pression de sorte que la seconde pression (5) faisant impact sur le second piston d'accumulation (3) agit sur la face arrière (F5) du premier piston d'accumulation (12) soumis à la haute pression.
  6. Réservoir selon la revendication 5, caractérisé en ce que la chambre (7) attenante à la face arrière du second piston (3) est reliée par un canal (8) à la pression environnante.
  7. Réservoir selon l'une des revendications 4 à 6, caractérisé en ce que la surface active (F2) pour la haute pression (4) du premier piston d'accumulation (12) de la première partie de tige de piston (15) est aussi grande que la surface active (F1) de la console (14) de la première partie de tige de piston (15) par rapport à la haute pression (4).
  8. Réservoir selon l'une des revendications 2 à 7, caractérisé en ce que la surface subissant l'impact de la seconde pression (5) du second piston d'accumulation (3) forme une butée pour la longueur la plus courte de la tige de piston rentrée (15, 16).
  9. Réservoir selon l'une des revendications 4 à 8, caractérisé en ce qu'à l'état rentré de la seconde partie de tige (16) quand elle s'applique contre la première partie de tige (15) par une butée, la surface de pression (F2) active, à ce moment, de la première partie de tige (15) est de la même dimension que la surface active (F1) de la seconde partie de tige (16) à l'état sorti de celle-ci.
  10. Réservoir selon l'une des revendications 2 à 9, caractérisé en ce que le premier piston d'accumulation (12) forme, en liaison avec une saillie (18) de l'enveloppe du réservoir (1), une butée pour la tige de piston.
  11. Réservoir selon l'une des revendications 1 à 10, caractérisé en ce que l'enveloppe est en aluminium.
  12. Réservoir selon l'une des revendications 1 à 10, caractérisé en ce que chaque piston d'accumulation (12, 3) constitue, avec les parties de tiges respectives (15, 16), une unité d'une seule pièce et est réalisé à partir de métal léger.
EP89114794A 1988-09-01 1989-08-10 Réservoir pour un circuit de fluide de pression, spécialement pour un circuit hydraulique d'avions Expired - Lifetime EP0356780B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3829646A DE3829646A1 (de) 1988-09-01 1988-09-01 Reservoir fuer einen druckmittelkreis, insbesondere flugzeughydraulikkreis
DE3829646 1988-09-01

Publications (3)

Publication Number Publication Date
EP0356780A2 EP0356780A2 (fr) 1990-03-07
EP0356780A3 EP0356780A3 (fr) 1991-05-29
EP0356780B1 true EP0356780B1 (fr) 1994-03-09

Family

ID=6362041

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EP89114794A Expired - Lifetime EP0356780B1 (fr) 1988-09-01 1989-08-10 Réservoir pour un circuit de fluide de pression, spécialement pour un circuit hydraulique d'avions

Country Status (2)

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EP (1) EP0356780B1 (fr)
DE (2) DE3829646A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110805577A (zh) * 2019-11-26 2020-02-18 燕山大学 一种气液分离式恒压压力油箱及控制方法

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2336633A (en) 1998-04-22 1999-10-27 Torotrak Dev Ltd Roller Control Unit for CVT
DE102004048822A1 (de) * 2004-10-07 2006-04-13 Continental Teves Ag & Co. Ohg Elektrohydraulisches Aggregat mit integriertem Druckmittelspeicher oder Druckmitteldämpfer
DE102007056684B4 (de) * 2007-11-24 2016-02-18 Schaeffler Technologies AG & Co. KG Druckspeicher
DE102010023016A1 (de) * 2010-06-08 2011-12-08 Hydac Technology Gmbh Hydraulische Anlage
US9127661B2 (en) * 2010-10-25 2015-09-08 Hamilton Sundstrand Corporation Bootstrap accumulator system with telescoping actuator cylinder
US8517040B2 (en) * 2011-08-12 2013-08-27 Hamilton Sundstrand Corporation Valve control of pump inlet pressure with bootstrap reservoir
US10570930B2 (en) 2011-10-10 2020-02-25 Angus Peter Robson Accumulator
WO2013054262A1 (fr) 2011-10-10 2013-04-18 Angus Peter Robson Accumulateur
US10578130B2 (en) 2013-04-18 2020-03-03 Hamilton Sundstrand Corporation Reservoir vent and thermal stabilization orifice
US20160160840A1 (en) * 2013-08-01 2016-06-09 Hydratech Industries Wing Power A/S Hydraulic pitch system utilizing pilot pressured reservoir for wind turbines
DE102014201663B4 (de) 2014-01-30 2016-08-04 Conti Temic Microelectronic Gmbh Vorrichtung zur pneumatischen Verstellung eines Sitzes in einem Verkehrsmittel, insbesondere in einem Kraftfahrzeug und Verkehrsmittel, insbesondere ein Kraftfahrzeug
CN104154051A (zh) * 2014-07-14 2014-11-19 中国商用飞机有限责任公司 一种油箱自增压装置
CN104329302B (zh) * 2014-10-10 2016-04-27 北京机械设备研究所 一种逐级增压油箱
CN104454764A (zh) * 2014-12-10 2015-03-25 中国航空工业集团公司金城南京机电液压工程研究中心 一种液压油箱双支撑结构
KR101714999B1 (ko) * 2015-02-16 2017-03-10 최창림 복동식 유압실린더
CN105333147A (zh) * 2015-11-25 2016-02-17 中国航空工业集团公司沈阳飞机设计研究所 一种气增压式液压油箱密封装置
US10920795B2 (en) * 2018-11-23 2021-02-16 The Boeing Company Bootstrap hydraulic reservoir
CN110307189A (zh) * 2019-05-23 2019-10-08 中国北方车辆研究所 一种为液压泵提供恒吸油压力的组件

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE929148C (de) * 1942-08-05 1955-06-20 Meiller Fahrzeuge Hydraulisch betaetigte Hub-, Kipp- und Rueckholpresse, insbesondere fuer Kraftfahrzeuge
FR2253160B1 (fr) * 1973-12-03 1977-06-24 Poclain Sa
DE2658488A1 (de) * 1976-12-23 1978-06-29 Emil Miller Druckmittel-kolbenzylinderanordnung
US4187682A (en) * 1979-01-02 1980-02-12 The Boeing Company Constant pressure hydraulic accumulator
DE3139600A1 (de) * 1981-10-06 1983-04-21 Gesellschaft für Hydraulik-Zubehör mbH, 6603 Sulzbach "kolbenspeicher"
DE8212164U1 (de) * 1982-04-28 1982-08-12 Gewerkschaft Eisenhütte Westfalia, 4670 Lünen Hydraulischer presszylinder fuer den rohrvorpressbetrieb
SU1236204A1 (ru) * 1984-10-12 1986-06-07 Всесоюзный Проектно-Технологический Институт Тяжелого Машиностроения Пневмогидравлический аккумул тор
DE3523717A1 (de) * 1985-07-03 1987-01-15 Daimler Berthold H Dr Dehnzylinder mit elastisch veraenderbarer laenge
DE3705642A1 (de) * 1986-07-02 1988-01-14 Man Nutzfahrzeuge Gmbh Energiespeicher- und abgabeeinrichtung

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
8705 Zusammenfassung Nr.035721,Q57,4.Februar 1987 & SU-A-1236204(HEAVY ENG TECH INST),7.Juni 1986 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110805577A (zh) * 2019-11-26 2020-02-18 燕山大学 一种气液分离式恒压压力油箱及控制方法

Also Published As

Publication number Publication date
EP0356780A3 (fr) 1991-05-29
DE58907166D1 (de) 1994-04-14
EP0356780A2 (fr) 1990-03-07
DE3829646A1 (de) 1990-03-15

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