EP0356780A2 - 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
EP0356780A2
EP0356780A2 EP89114794A EP89114794A EP0356780A2 EP 0356780 A2 EP0356780 A2 EP 0356780A2 EP 89114794 A EP89114794 A EP 89114794A EP 89114794 A EP89114794 A EP 89114794A EP 0356780 A2 EP0356780 A2 EP 0356780A2
Authority
EP
European Patent Office
Prior art keywords
pressure
piston
partial
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.)
Granted
Application number
EP89114794A
Other languages
German (de)
English (en)
Other versions
EP0356780B1 (fr
EP0356780A3 (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
Alfred Teves 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, Alfred Teves 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

  • 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-OS 19 26 410.
  • DE-OS 18 04 037 deals 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 working 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.
  • Reservoir has limited space available.
  • the invention is therefore based on a reservoir of the type described in the preamble of the main claim.
  • the object of the invention is to construct such a reservoir in a space-saving manner.
  • the invention is solved by the combination of features resulting from the characterizing part of the main claim.
  • the invention therefore consists in making the piston rod, which connects the two pistons together, collapsible, so that their length can be adapted to the respective pressure requirements.
  • 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 changes their position first as a function of the applied pressures depends on the geometric dimensions of the effective pressure surfaces on the first piston and on the piston surfaces of the intermediate space, which are formed by the sealingly guided brackets.
  • the interior of the sleeve-shaped partial rods to be moved into one another is also used for storing the Low pressure medium used.
  • the space above the first partial rod can also be used as a low-pressure space if the partial rods are in a corresponding position.
  • the first partial piston rod only begins its movement relative 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 moving up into it has reached its end position. If the second partial rod is attached to the first partial rod, they form a one-piece part in which the space formed by the two partial rods can no longer develop dynamic forces and thus forms a closed, no longer expandable space.
  • a combination of features according to claim 8 describes an expedient embodiment of a stop for the second partial piston rod on the first partial piston rod.
  • the housing of the reservoir 1 is divided into a first pressure chamber 4 and a second pressure chamber 5.
  • the two working 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 working piston 3, is connected to the ambient pressure via an opening 8.
  • the chamber 9 located above the first working 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 chambers 5 and 9.
  • the first pressure chamber 4 used for storing 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 delivers 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 in that the piston rod 6 of the first working piston 2 takes the second working piston 3 in FIG. 1 upwards 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 working 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 modules of the same value as in FIG. 1 being given the same reference numerals.
  • the reservoir is rotationally symmetrical, but circumferential edges have been omitted for reasons of greater clarity.
  • 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 to the ambient pressure via an opening 8, 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, reaches the low-pressure chamber 5 via the low-pressure inlet 22 and is led to the inlet of the pump 10 via a second, not shown, low-pressure outlet. 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), which is composed of two sleeve-shaped partial rods 15, 16, which are telescopically displaceable, is essential for the invention.
  • the first partial rod 15 carries the first working piston 12 at its upper end in FIG. 2, while the second partial rod 16 is connected in one piece to the second working piston 3 at its lower end in the 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 at the same time 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 by 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 pressure-medium-permeable support 25.
  • the ratio of the effective areas F1 and F2 is decisive for the movement of the two partial bars 15 and 16 against one another or with one another and for the course of this movement.
  • 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, the ring F1 with the smaller diameter naturally having to 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, so 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 effective area of the access channel 17 is also not one because of the same areas F4, F5 Contribute movement of the first partial rod 15.
  • the movement of the piston rod 15, 16 is therefore only caused by the movement of the second partial rod 16, for example by this second partial rod moving up 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, takes the first partial rod 15 on its way up.
  • the frictional forces of the seal on the partial rods are neglected or taken into account that the frictional forces of the seals with the larger circumference, which act on the outer surface of the first partial rod 15, are greater than the frictional forces of the brackets 13 and 14.
  • FIG. 3 A possible movement sequence 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 working 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 on, the first part of the piston 15 stops and the second part of the piston 16 starts to move upward within the first part of the piston 15. If a force balance between the high pressure pressing on the surface F1 and the low pressure acting on the working piston 3 is already reached during this path, the piston 16 remains at the relevant point within the piston 15, while the piston 15 in FIG. 3 is in its position does not change.
  • FIG. 4 shows the position of the second partial rod in which it strikes the lower part of the first partial rod 15 by means of the second working piston 3.
  • the two partial rods 15 and 16 pushed into one another move upwards together by the second partial rod 16 taking the first partial rod 15 with them, provided that a corresponding pressure in the second pressure chamber 5 does not ensure a corresponding force compensation, so that the two partial bars remain shifted into each other.
  • the working piston pulls the second partial rod 16 back down a suitable distance, 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.

Landscapes

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

Family

ID=6362041

Family Applications (1)

Application Number Title Priority Date Filing Date
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)

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

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999054646A1 (fr) * 1998-04-22 1999-10-28 Torotrak (Development) Limited Unite de commande de rouleaux pour transmission a rapport variable en continu
DE102004048822A1 (de) * 2004-10-07 2006-04-13 Continental Teves Ag & Co. Ohg Elektrohydraulisches Aggregat mit integriertem Druckmittelspeicher oder Druckmitteldämpfer
US20120097021A1 (en) * 2010-10-25 2012-04-26 Short Keith E Bootstrap accumulator system with telescoping actuator cylinder
EP2792887A1 (fr) * 2013-04-18 2014-10-22 Hamilton Sundstrand Corporation Évent de réservoir et orifice de stabilisation thermique
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
CN104329302A (zh) * 2014-10-10 2015-02-04 北京机械设备研究所 一种逐级增压油箱
WO2015014367A1 (fr) * 2013-08-01 2015-02-05 Hydratech Industries Wind Power A/S Système de pas hydraulique utilisant un réservoir pressurisé pilote pour turbines éoliennes
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
KR20160101256A (ko) * 2015-02-16 2016-08-25 최창림 복동식 유압실린더
EP2557314A3 (fr) * 2011-08-12 2016-11-09 Hamilton Sundstrand Corporation Commande de soupape d'entrée de pompe d'un réservoir pressurisé
US9790962B2 (en) 2011-10-10 2017-10-17 Angus Peter Robson Accumulator
CN110529451A (zh) * 2018-05-24 2019-12-03 空中客车德国运营有限责任公司 用于液压系统的储存器
US10570930B2 (en) 2011-10-10 2020-02-25 Angus Peter Robson Accumulator
EP3657026A1 (fr) * 2018-11-23 2020-05-27 The Boeing Company Réservoir hydraulique d'amorçage

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
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
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
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
CN110805577B (zh) * 2019-11-26 2021-04-27 燕山大学 一种气液分离式恒压压力油箱及控制方法

Family Cites Families (8)

* 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
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

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6273839B1 (en) 1998-04-22 2001-08-14 Torotrak (Development) Limited Roller control unit for a continuously-variable-ratio transmission
WO1999054646A1 (fr) * 1998-04-22 1999-10-28 Torotrak (Development) Limited Unite de commande de rouleaux pour transmission a rapport variable en continu
DE102004048822A1 (de) * 2004-10-07 2006-04-13 Continental Teves Ag & Co. Ohg Elektrohydraulisches Aggregat mit integriertem Druckmittelspeicher oder Druckmitteldämpfer
US20120097021A1 (en) * 2010-10-25 2012-04-26 Short Keith E Bootstrap accumulator system with telescoping actuator cylinder
US9127661B2 (en) * 2010-10-25 2015-09-08 Hamilton Sundstrand Corporation Bootstrap accumulator system with telescoping actuator cylinder
EP2557314A3 (fr) * 2011-08-12 2016-11-09 Hamilton Sundstrand Corporation Commande de soupape d'entrée de pompe d'un réservoir pressurisé
US10570930B2 (en) 2011-10-10 2020-02-25 Angus Peter Robson Accumulator
US9790962B2 (en) 2011-10-10 2017-10-17 Angus Peter Robson Accumulator
EP2792887A1 (fr) * 2013-04-18 2014-10-22 Hamilton Sundstrand Corporation Évent de réservoir et orifice de stabilisation thermique
US10578130B2 (en) 2013-04-18 2020-03-03 Hamilton Sundstrand Corporation Reservoir vent and thermal stabilization orifice
WO2015014367A1 (fr) * 2013-08-01 2015-02-05 Hydratech Industries Wind Power A/S Système de pas hydraulique utilisant un réservoir pressurisé pilote pour turbines éoliennes
CN105473848A (zh) * 2013-08-01 2016-04-06 海卓泰克工业风力有限公司 用于风力涡轮机的利用先导式加压储存器的液压变桨距系统
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
CN104329302A (zh) * 2014-10-10 2015-02-04 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
KR20160101256A (ko) * 2015-02-16 2016-08-25 최창림 복동식 유압실린더
CN110529451A (zh) * 2018-05-24 2019-12-03 空中客车德国运营有限责任公司 用于液压系统的储存器
EP3657026A1 (fr) * 2018-11-23 2020-05-27 The Boeing Company Réservoir hydraulique d'amorçage
US10920795B2 (en) 2018-11-23 2021-02-16 The Boeing Company Bootstrap hydraulic reservoir
AU2019268152B2 (en) * 2018-11-23 2025-01-23 The Boeing Company Bootstrap hydraulic reservoir

Also Published As

Publication number Publication date
EP0356780B1 (fr) 1994-03-09
EP0356780A3 (fr) 1991-05-29
DE58907166D1 (de) 1994-04-14
DE3829646A1 (de) 1990-03-15

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