WO1985004455A1 - Systeme hydraulique pour vehicules - Google Patents

Systeme hydraulique pour vehicules Download PDF

Info

Publication number
WO1985004455A1
WO1985004455A1 PCT/EP1985/000117 EP8500117W WO8504455A1 WO 1985004455 A1 WO1985004455 A1 WO 1985004455A1 EP 8500117 W EP8500117 W EP 8500117W WO 8504455 A1 WO8504455 A1 WO 8504455A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
hydraulic system
pressure
feed pump
control valve
Prior art date
Application number
PCT/EP1985/000117
Other languages
German (de)
English (en)
Inventor
Hamma Karlmann
Original Assignee
Zahnradfabrik Friedrichshafen Ag
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 Zahnradfabrik Friedrichshafen Ag filed Critical Zahnradfabrik Friedrichshafen Ag
Publication of WO1985004455A1 publication Critical patent/WO1985004455A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/22—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves
    • F04B49/225—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00 by means of valves with throttling valves or valves varying the pump inlet opening or the outlet opening

Definitions

  • the invention relates to a hydraulic system for vehicles, in particular for working hydraulics in forklifts, loaders and the like, with an suction-controlled feed pump, with consumers that can be activated via control valves, and with a pressure relief valve.
  • Suction-controlled feed pumps have already been proposed for hydraulic systems in which, in the idle state, they only offer a low pressure which is small in relation to the maximum pressure. This measure is intended to save energy.
  • the disadvantage here is that the system pressure is limited by a pressure relief valve and no adjustment of the intake flow to the feed pump is possible.
  • Hydraulic systems with pressure regulators are also known which offer a constant pressure in the hydraulic system within the control range of the pump.
  • the pump thus only pumps as much hydraulic fluid as is consumed by the consumers.
  • a combined pressure-flow control by corresponding control valves is also known.
  • a constant flow rate with variable drive speed can be achieved.
  • the adjustment takes place via the differential pressure of a variable or constant orifice installed in the working line.
  • a disadvantage of these known hydraulic systems is that they are relatively complex and expensive. For example, two pressure control valves are required for pressure-flow control and regulation can only be achieved if a more complex feed pump with an adjusting device is available, through which the flow can be regulated.
  • the present invention is therefore based on the object of providing a hydraulic system of the type mentioned at the outset, in which the delivery flow can be adjusted in a simple manner in a suction-regulated delivery pump in such a way that the delivery results in accordance with the desired requirements, at the same time, even if the flow rate is not required, it drops back to a minimum value (pilot flow) and also enables stepless control.
  • the feed pump is now controlled as a function of the differential pressure which is generated at the measuring throttle.
  • This control takes place via the control valve located in front of the feed pump.
  • a simple feed pump can be used as the feed pump without the need for a separate adjusting device for regulating the feed flow.
  • the control of the feed pump does not react to the system pressure itself, but to the pressure difference, another very great advantage is achieved.
  • the power consumption of the pump is therefore no longer dependent on its maximum possible power consumption, but rather its power consumption is automatically based on the respective conditions. This means that considerable energy savings are achieved and the system itself can also be designed more simply.
  • the power consumption of the pump can be reduced to a minimum value if both the flow rate and the pressure are kept low.
  • pilot current a minimum current as so-called pilot current will always be necessary because behind the "erfindungsge ⁇ MAESSEN orifice pressure should be always present, so that the control valve can address.
  • a pressure relief valve known per se can be arranged for the pump and upstream of the measuring throttle, via which the pilot flow flows out with minimal delivery.
  • the pilot flow can optionally also be derived via one of the consumers. If, for example, one of the consumers is a hydrostatic power steering system with an open center, which itself always requires a minimal delivery rate, the pilot current can thus be conducted via this consumer.
  • the pressure relief valve of the steering control is set to a lower pressure.
  • the flow rate can be regulated continuously in the control valve. All that is required is a corresponding design of the control valve, which is known per se.
  • FIG. 2 shows a longitudinal section through a swash plate pump with a control valve according to the invention integrated in a flanged housing and a measuring throttle
  • J shows a longitudinal section through the control valve according to the invention.
  • a pump 1 sucks the hydraulic fluid from a container 2 via a suction connection S, a control valve 3 and the channel S 1 .
  • the hydraulic fluid is conducted to the consumer via a measuring throttle 4, which is fixed or, if necessary, also adjustable.
  • Consumer 5, eg a steering system, and consumers 6, eg a working hydraulic system, are switched via associated valves 5a and 6a.
  • a priority valve 7 supplies the steering primarily with oil.
  • the hydraulic fluid delivered by the feed pump 1 generates a pressure difference at the throttle inlet 8 and at the throttle outlet 9 when passing through the measuring throttle 4.
  • Measuring throttle 4 shows a pressure drop with pressure difference between the throttle input 8 and the throttle output 9. This pressure difference switches the control valve to passage depending on the pressure forces at 1 and at x ? , as well as the closing force of a spring 10.
  • the pump 1 can now suck in hydraulic fluid to the appropriate extent and make the desired quantity available to the consumers 5 and / or 6.
  • the system pressure is limited via a pressure limiting valve 11 or set via the load on the consumer.
  • the consumer with the highest working pressure determines the pressure level of the pump.
  • This circuit contributes significantly to reducing the energy consumption when compared to the known use of constant pumps or suction-controlled pumps, which in the known systems take up power depending on the speed.
  • the power consumption when the consumers are switched off is further reduced to the pure idle power of the pump.
  • the pump 1 is shown as a swash plate pump, the "control valve 3 and the measuring throttle 4 are integrated to the in a housing 12.
  • the points S, S ', P, x .. and x -.. specified structure and Wir ⁇ of action of a swash plate pump are generally be ⁇ known, it is considered why not subsequently Silicon ⁇ here in greater detail it can be seen that maintain distributed over the circumference delivery piston 15 of the pump 1 via "S 1". and the hydraulic fluid has a bore 13.
  • a swash plate 14 provides for the stroke of the delivery pistons 15 in the usual way.
  • the delivery pistons 15 are connected to one another on their pressure side by means of associated check valves 20 in an annular space 16 the measuring throttle 4 is then the measuring point 8, while the measuring point 9 is located behind the measuring throttle.
  • control valve 3 is shown, with which a continuous control of the flow rate is possible. Also in this figure are again for better explanation
  • the crizven il has two pistons 17 and 18, the effective piston areas at 1 and x - must be the same size. If the housing is designed accordingly, the pistons can also be made in one piece.
  • the piston 18 is provided with at least one bore 19 on its circumference, which can be made to coincide with the pump inlet S '. Depending on the pressure differences present, an overlap or shut-off is achieved by the position of the piston 17 or 18. To shut off the S pump inlet S ', the piston 17 is correspondingly shifted to the right in FIG. 3, whereby the piston 18 is also shifted to the right so far that the illustrated shut-off position is reached. Conversely, an opening movement is initiated at a higher pressure at x "on the piston 18, taking into account the closing force of the spring 10.

Abstract

Un système hydraulique pour des véhicules, en particulier l'hydraulique de travail des empileuses à fourches, des chargeuses et autres, est doté d'une pompe d'alimentation à réglage de l'aspiration (1) avec des dispositifs de consommation (5, 6) raccordables par des vannes-pilotes (5a, 6a) et avec un limiteur de pression (11). Dans la direction d'alimentation, avant la pompe d'alimentation (1), est disposée une vanne de réglage (3), alors qu'un étranglement de mesure (7) est placé après la pompe (1) et avant les vannes-pilotes (5a, 6a), les surfaces de piston effectives pour la différence de pression créée par l'étranglement de mesure étant de même grandeur dans la vanne de réglage (3) et ladite vanne de réglage étant commutable en fonction de la différence de pression avec un ressort de fermeture sur le passage ou dans la direction de fermeture.
PCT/EP1985/000117 1984-03-29 1985-03-19 Systeme hydraulique pour vehicules WO1985004455A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
LUPCT/EP84/00087 1984-03-29
EP8400087 1984-03-29

Publications (1)

Publication Number Publication Date
WO1985004455A1 true WO1985004455A1 (fr) 1985-10-10

Family

ID=8164933

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP1985/000117 WO1985004455A1 (fr) 1984-03-29 1985-03-19 Systeme hydraulique pour vehicules

Country Status (2)

Country Link
DE (1) DE3509856A1 (fr)
WO (1) WO1985004455A1 (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0255681A2 (fr) * 1986-08-04 1988-02-10 General Signal Corporation Système de contrôle de débit pour une pompe hydraulique
EP0288826A1 (fr) * 1987-04-24 1988-11-02 Vickers Incorporated Système hydraulique à débit d'entrée réduit
FR2653500A1 (fr) * 1989-10-24 1991-04-26 Daimler Benz Ag Dispositif pour commander la pression dans un systeme de pression hydraulique.
JP2010503798A (ja) * 2006-09-14 2010-02-04 ルーク ラメレン ウント クツプルングスバウ ベタイリグングス コマンディートゲゼルシャフト 消費器に作動液を供給するための液圧系
EP1903238A3 (fr) * 2006-09-21 2010-11-10 LuK Lamellen und Kupplungsbau Beteiligungs KG Système hydraulique
TWI796502B (zh) * 2019-07-05 2023-03-21 金德創新技術股份有限公司 雙動力源複合控制裝置

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2625560B2 (ja) * 1988-09-15 1997-07-02 ツァーンラートファブリーク、フリードリッヒスハーフェン、アクチエンゲゼルシャフト ラジアルピストンポンプ
US5167493A (en) * 1990-11-22 1992-12-01 Nissan Motor Co., Ltd. Positive-displacement type pump system
DE4209143C1 (fr) * 1992-03-20 1993-04-15 Siegfried A. Dipl.-Ing. 7960 Aulendorf De Eisenmann
DE4408628C2 (de) * 1994-03-09 1996-11-28 Claas Ohg Lenkventil
DE4432263C2 (de) * 1994-09-10 1996-07-11 Walterscheid Gmbh Gkn Kombinationsventil für sauggedrosselte Hydraulikpumpen
DE19510206B4 (de) * 1995-03-21 2005-08-18 Zf Friedrichshafen Ag Regeleinrichtung für einen Hydraulikkreis
DE19612412B4 (de) * 1996-03-28 2006-07-06 Siemens Ag Regelung für ein Druckfluid-Versorgungssystem, insbesondere für den Hochdruck in einem Kraftstoff-Einspritzsystem
DE19612413B4 (de) * 1996-03-28 2006-06-29 Siemens Ag Druckfluid-Versorgungssystem, insbesondere für ein Kraftstoff-Einspritzsystem
DE19708597C1 (de) * 1997-03-03 1999-01-28 Luk Fahrzeug Hydraulik Sauggedrosselte Förderpumpe
US6647965B1 (en) 2003-01-08 2003-11-18 Robert H. Breeden Pump assembly and method
DE102011050806A1 (de) 2011-06-01 2012-12-06 Continental Reifen Deutschland Gmbh Kompressor mit Druckbegrenzung

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1293409A (fr) * 1961-06-27 1962-05-11 Integral Ltd Perfectionnements aux pompes à mouvement alternatif
FR2052832A5 (fr) * 1969-06-25 1971-04-09 Task Corp
FR2204231A5 (fr) * 1972-10-23 1974-05-17 Ifield Richard
GB2054757A (en) * 1979-07-25 1981-02-18 Zahnradfabrik Friedrichshafen High-pressure pump with pressure regulator

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1293409A (fr) * 1961-06-27 1962-05-11 Integral Ltd Perfectionnements aux pompes à mouvement alternatif
FR2052832A5 (fr) * 1969-06-25 1971-04-09 Task Corp
FR2204231A5 (fr) * 1972-10-23 1974-05-17 Ifield Richard
GB2054757A (en) * 1979-07-25 1981-02-18 Zahnradfabrik Friedrichshafen High-pressure pump with pressure regulator

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0255681A2 (fr) * 1986-08-04 1988-02-10 General Signal Corporation Système de contrôle de débit pour une pompe hydraulique
EP0255681A3 (fr) * 1986-08-04 1990-02-07 General Signal Corporation Système de contrôle de débit pour une pompe hydraulique
EP0288826A1 (fr) * 1987-04-24 1988-11-02 Vickers Incorporated Système hydraulique à débit d'entrée réduit
FR2653500A1 (fr) * 1989-10-24 1991-04-26 Daimler Benz Ag Dispositif pour commander la pression dans un systeme de pression hydraulique.
JP2010503798A (ja) * 2006-09-14 2010-02-04 ルーク ラメレン ウント クツプルングスバウ ベタイリグングス コマンディートゲゼルシャフト 消費器に作動液を供給するための液圧系
EP1903238A3 (fr) * 2006-09-21 2010-11-10 LuK Lamellen und Kupplungsbau Beteiligungs KG Système hydraulique
TWI796502B (zh) * 2019-07-05 2023-03-21 金德創新技術股份有限公司 雙動力源複合控制裝置

Also Published As

Publication number Publication date
DE3509856A1 (de) 1985-10-10

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