EP0904467A1 - Commande de mecanisme rotatif a systeme d'alimentation - Google Patents

Commande de mecanisme rotatif a systeme d'alimentation

Info

Publication number
EP0904467A1
EP0904467A1 EP97918141A EP97918141A EP0904467A1 EP 0904467 A1 EP0904467 A1 EP 0904467A1 EP 97918141 A EP97918141 A EP 97918141A EP 97918141 A EP97918141 A EP 97918141A EP 0904467 A1 EP0904467 A1 EP 0904467A1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
valve
hydraulic
pilot
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
EP97918141A
Other languages
German (de)
English (en)
Other versions
EP0904467B1 (fr
Inventor
Reinhold Schniederjan
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik 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 Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP0904467A1 publication Critical patent/EP0904467A1/fr
Application granted granted Critical
Publication of EP0904467B1 publication Critical patent/EP0904467B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/08—Superstructures; Supports for superstructures
    • E02F9/10—Supports for movable superstructures mounted on travelling or walking gears or on other superstructures
    • E02F9/12—Slewing or traversing gears
    • E02F9/121—Turntables, i.e. structure rotatable about 360°
    • E02F9/123—Drives or control devices specially adapted therefor
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/08—Superstructures; Supports for superstructures
    • E02F9/10—Supports for movable superstructures mounted on travelling or walking gears or on other superstructures
    • E02F9/12—Slewing or traversing gears
    • E02F9/121—Turntables, i.e. structure rotatable about 360°
    • E02F9/128—Braking systems
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2285—Pilot-operated systems
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement 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
    • 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

Definitions

  • the invention relates to a hydraulic control, in particular for controlling the slewing gear of an excavator.
  • a hydraulic control according to the preamble of claim 1 goes e.g. from DE 44 05 472 AI.
  • the hydraulic circuit diagram of this known hydraulic control is reproduced for better understanding of the invention in Figure 2 of the drawing and is briefly described below with reference to Figure 2.
  • the known slewing gear control 1 shown in FIG. 2 comprises a drive hydraulic pump 2, which is connected via working lines 3, 4 to a drive hydraulic motor, not shown, for driving the also not shown slewing gear of an excavator.
  • the hydraulic control comprises a manual control transmitter 5, which is connected to a pilot control device 8 via control lines 6 and 7.
  • an adjusting device 9 is supplied with the necessary signal pressure, which is obtained directly from the control pressure prevailing in the control lines 6, 7.
  • the adjusting device comprises a control piston 12 which is arranged between two control pressure chambers 10 and 11 and which acts on the displacement volume of the working hydraulic pump 2.
  • the filter must be dimensioned relatively large, which is contrary to the goal of a small size of the hydraulic control.
  • the suction filter 16 must be cleaned and serviced regularly.
  • the invention is based on the knowledge that when the actuating pressure for the adjusting device is obtained from the feed pressure made available by the feed device, two goals are achieved simultaneously. On the one hand, it is ensured that after resetting the manual control transmitter and thus also the pilot control device, filtered pressure fluid flows into its respective neutral position to compensate for the volume differences during the resetting process into the actuating pressure chambers of the adjusting device. There is no need for a suction device. On the other hand, it is ensured that in the event of a failure of the feed device, e.g. by clogging the feed filter, no signal pressure is available and thus the working hydraulic pump swings back into its neutral position. Damage to the working hydraulic pump and the working hydraulic motor in the event of this fault is thus reliably avoided.
  • the pilot control device can be designed in a manner known per se as a 4/3-way valve. However, it is more advantageous, according to claim 3, to separately design the pilot control device with separate valve areas for one control pressure chamber of the adjusting device. This enables separate control of the right and left swiveling of the slewing gear. If, in this arrangement, dirt particles should nevertheless penetrate into the valve of the pilot control device and should block it in one of its control positions, it is ensured that when the control direction is changed by means of the manual control device and the pressure in the control lines 6 and 7 is reversed accordingly, there is no unintentional acceleration of the slewing gear in the opposite direction he follows. In this case, the pilot control device can be designed as a 6/3-way valve.
  • the pressure control valve provided between the feed device and the pilot control device or the two pressure control valves provided for separate control of the right and left swiveling according to claim 3 can set the signal pressure to the control pressure prevailing in the control line or a slightly higher pressure.
  • the pressure difference between the control pressure and the signal pressure can be achieved by spring loading of the pressure control valve or the pressure control valves.
  • a pressure cut-off valve can be provided between the control pressure lines and the pressure fluid tank in order to limit the pressure in the control lines to a predetermined maximum pressure.
  • a brake valve can be provided to enable slow, decelerated braking of the slewing gear.
  • FIG. 1 shows a first embodiment of the hydraulic system according to the invention
  • Fig. 3 shows a second exemplary embodiment of the hydraulic according to the invention
  • FIG. 1 shows a first exemplary embodiment of the hydraulic control 1 according to the invention.
  • the slewing gear is driven by a hydraulic drive motor, not shown, which is located in a hydraulic working circuit formed by the working lines 3 and 4, which is supplied by the working hydraulic pump 2.
  • the leakage losses are replenished into the hydraulic circuit 3, 4 by means of the feed device 19, which comprises a feed pump 20.
  • the feed pump 20 is coupled to the working hydraulic pump 2 and sucks in pressure fluid from the pressure fluid tank 18 via the feed filter 18 and feeds it into the feed line 30.
  • the feed line 30 is connected via check and pressure control valves 31 and 32 to the working lines 3 and 4 in order to feed the pressure fluid into the respective low-pressure working line 3 or 4. This ensures that there is sufficient pressure fluid in the working circuit 3, 4 as the working medium.
  • a pressure relief valve 33 is also provided, which connects the feed line 30 to the pressurized fluid tank 17.
  • the working hydraulic pump 2 is controlled manually by the operator via the manual control transmitter 5, which is connected to a control pressure feed 35 via a control line filter 34.
  • the manual control transmitter 5 supplies a control pressure to one of the two control lines 6 or 7, the level of which is proportional to the intended torque.
  • the respective other control line 7 or 6 is ventilated via the tank line 36.
  • control lines 6 and 7 are led via throttling points 37 and 38 to the pilot chambers 39 and 40 of the pilot device 8.
  • the pressure difference between the pilot chambers 39 and 40 causes a displacement of the valve body 41
  • Pilot control device 8 in one of the two control positions 42 and 43, depending on which of the control lines 6 and 7 is acted upon by the control pressure.
  • one of the signal pressure chambers 10 and 11 is acted upon by a signal pressure, while the other signal pressure chamber 11 and 10, respectively, via the tank line 44 and the brake valve 45 to be described in more detail with the pressure fluid Tank 17 is connected.
  • the associated displacement of the actuating piston 12 causes the working hydraulic pump 2 to be deflected in the desired conveying direction, so that the hydraulic motor (not shown) and the rotating mechanism driven by it are accelerated in the intended direction of rotation.
  • For the mechanical return device 46 a return force proportional to the adjustment of the actuating piston 12 from its neutral position is applied to the
  • Pilot control device 8 exercised, where this is basically known from DE-OS 41 25 706. Furthermore, compensation lines 47 and 48 connected to the working lines 3 and 4 are provided, so that the pressure difference between the working lines 3 and 4 has a force-compensating effect on the displacement of the valve body 41 of the pilot control device 8.
  • a pressure cut-off valve 50 is arranged between a shuttle valve 49 connected to the control pressure lines 6 and 7 and the pressure fluid tank 17.
  • the pressure cut-off valve 50 effects a pressure limitation of the control pressure prevailing in the respective pressure-carrying control pressure line 6 or 7, the maximum pressure being predeterminable via the electromagnetic transmitter 51.
  • a brake valve 45 is also provided, which enables controlled and sensitive braking.
  • the brake valve 45 is arranged between the tank line 44 connected to the pilot control device 8 and the pressurized fluid tank 17.
  • the brake valve 45 is acted upon via the control pressure connecting line 52 and the shuttle valve 49 on the one hand by the control pressure prevailing in the control lines 6 and 7 and on the other hand via the working pressure connecting line 53 and the shuttle valve 54 by the working pressure prevailing in the high-pressure side working line 3 and 4.
  • the signal pressure is not obtained directly from the control pressure lines 6 and 7, but indirectly via a pressure relief valve 56 from the feed pressure prevailing in the feed line 30.
  • the pilot control device 8 is connected to the feed line 30 via an actuating pressure line 57, the pressure control valve 56 and the throttle point 58.
  • the pressure control valve 56 regulates the control pressure prevailing in the control pressure line 57 to a pressure level that results from the balance of forces between the control pressure of the respective pressure-carrying control pressure line 6 or 7, which is brought about via the control pressure connecting line 52 and the shuttle valve 49, and the spring action by the compression spring 59 on the one hand and the control pressure brought in via the detour line 60 on the other.
  • a control pressure is set in the control pressure line 57, which is slightly higher than the control pressure prevailing in the pressure-carrying control pressure line 6 or 7 due to the spring action by the compression spring 59.
  • the pressure difference between the signal pressure and the control pressure is preferably 1 to 2 bar and is adjustable via the adjustable pressure spring 59.
  • the actuating pressure chambers 10 and 11 of the adjusting device 9 are connected to the pressure control valve 56 with the Feed line 30 connected.
  • the compression spring 59 ensures that pressure fluid can flow into the actuating pressure chambers 10 and 11 via the actuating pressure line 57 and the pilot control device 8 when the pusher piston 12 is pushed back into its neutral central position due to the return springs 13 and 14.
  • the pressure fluid required for volume equalization in the actuating pressure chambers 10 and 11 is therefore not, according to the development according to the invention, via a
  • the further development according to the invention ensures that always filtered oil is supplied from the feed line 30 to the pilot control device 8 and the adjusting device 9. This reliably prevents contamination of these devices. Furthermore, a suction device with a relatively large suction filter can be dispensed with, so that the hydraulic control according to the invention can be designed to be structurally more compact. The adjustment device is also continuously supplied with oil.
  • FIG. 3 shows another Ausruhrungsbeispiel the invention with an additional training.
  • the elements already described with reference to FIG. 1 are included Matching reference numerals, so that a repeated description in this regard is unnecessary.
  • the valve body 41 of the pilot control device 8 has separate valve regions 42a, 61a, 43a and 42b, 61b and 43b.
  • the valve area 42a, 61a, 43a with the control positions 42a and 43a and the neutral position 61a serves to control the signal pressure chamber 11.
  • the valve area 42b, 61b, 63b with the control positions 42b and 43b and the neutral position 61b for controlling the control pressure chamber 10.
  • the two valve areas are accommodated in a uniform valve body 41.
  • the function of this 6/3-way valve is largely the same as that of the 4/3-way valve, which is used in the embodiment of Figure 1.
  • a separate pressure control valve 56a and 56b is provided for each valve region of the pilot control device 8, both of which are connected to the feed line 30 via the throttle point 58.
  • the pressure control valve 56a essentially adjusts the pressure in the control pressure line 57a to the control pressure specified by the control line 6, the pressure in the control pressure line 57a being due to the
  • Compression spring 59a is slightly larger than the control pressure in the control line 6. The same applies to the pressure control valve 56b, the control pressure in the control pressure line 57b being essentially regulated to the control pressure prevailing in the control line 7, but due to the compression spring 59b being slightly greater than the control pressure prevailing in the control line 7.
  • the separation of the control for the right and left swiveling has the advantage that if the pilot control device 8 is blocked due to the penetration of dirt particles, no dangerous malfunction occurs. While in the exemplary embodiment according to FIG. 1 in the same way as in the prior art shown in FIG. 2, the pilot control device 8 is blocked in one of its control positions 42 or 43 and a subsequent print page change In the control lines 7 and 6, a further pivoting of the slewing gear without causing the intended change of direction of rotation is caused, this fault condition is avoided in the embodiment according to FIG. 3. If, in the exemplary embodiment according to FIG.
  • the pilot control device 8 is blocked in one of its control positions, for example in the control position 42a and 42b, this means that the control chamber 11 via the pressure control valve 56a with the feed line 30 and the control chamber 10 via the tank line 44 communicates with the pressure fluid tank 17. If the control line 7 is acted upon by control pressure 7 instead of the control line 6 as a result of an intended change in the direction of rotation of the controlled slewing gear, the drive hydraulic pump 2 does not swivel out again, because the connection to the control pressure line 57b is due to the blocking of the pilot control device 8 cut off in the control position 42b. The actuating pressure chamber 10 is not subsequently acted upon by actuating pressure in this fault state. In contrast to the exemplary embodiment according to FIG.
  • the actuating pressure chamber 11 is not inadvertently acted upon by actuating pressure since the actuating pressure chamber 11 is connected to the actuating pressure line 57a via the pilot control device 8 blocked in the control position 42a.
  • the control pressure line 57a is essentially depressurized, since the control pressure prevailing in the control pressure line 57a is predetermined by the control pressure prevailing in the control line 6 via the pressure control valve 56a. Since the control line 6 is depressurized after reversing the intended direction of rotation, there is no faulty pivoting out of the hydraulic drive pump 2 in the unintended original conveying direction. This effectively prevents the slewing gear from accelerating in the unintended direction of rotation.
  • FIG. 4 shows an exemplary embodiment of one of the pressure control valves 56, 56a and 56b used in the context of the present invention.
  • the actuating pressure line 57 is connected to the pressure fluid tank 17 via a first control edge 70 and to the feed line 30 via a second control edge 71.
  • a first pressure chamber 72 is connected via the control pressure connection line 52 to one of the control lines 6 and 7, while a second pressure chamber 73 is connected to the control pressure line 57 via a detour line 60.
  • a preferably adjustable compression spring 59 is also provided in the first pressure chamber 72. Due to the force equilibrium that is established, the pressure in the control pressure line 57 is set to a slightly higher pressure than the control pressure prevailing in the control pressure connecting line 52. The difference between the control pressure prevailing in the control pressure line 57 and the control pressure specified via the control pressure connection line 52 corresponds to the additional force caused by the compression spring 59.
  • the pressure difference between the control pressure and the control pressure is preferably 1 to 2 bar.
  • the invention is not limited to the exemplary embodiments shown.
  • the specific configurations of the pilot control device and the adjusting device can also be of a different type within the scope of the present invention.
  • Known pressure control valves of any design can be used as pressure control valves 56, 56a and 56b.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne une commande hydraulique, notamment pour le mécanisme rotatif d'un excavateur. Dans un circuit d'entraînement, une pompe hydraulique d'entraînement (2) et un moteur hydraulique d'entraînement sont reliés par l'intermédiaire de conduites de travail (4, 3). Cette commande hydraulique comprend un dispositif de réglage (9) pour régler un piston de régulation monté entre deux chambres de pression de régulation (10, 11) et agissant sur le volume de refoulement d'une pompe hydraulique d'entraînement (2). D'autre part, une unité de pilotage (8) applique une pression de régulation à l'une des chambres de pression de régulation (10, 11) en fonction de la différence de pression entre deux conduites de commande (6, 7). Conformément au perfectionnement selon l'invention, l'unité de pilotage (8) est reliée à une conduite d'alimentation (30) par l'intermédiaire d'une soupape de régulation de pression (56) et, dans une position de pilotage (42, 43), elle relie une des deux chambres de pression de régulation (10, 11) à la conduite d'alimentation (30) par l'intermédiaire de la soupape de régulation de pression (56) et l'autre chambre (11, 10) à un réservoir de fluide sous pression (17). Dans une position neutre (61), les deux chambres de pression de régulation (10, 11) sont reliées à la conduite d'alimentation (30) par l'intermédiaire de la soupape de régulation de pression (56).
EP97918141A 1996-05-22 1997-04-17 Commande de mecanisme rotatif a systeme d'alimentation Expired - Lifetime EP0904467B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19620665A DE19620665C1 (de) 1996-05-22 1996-05-22 Hydraulische Steuerung, insbesondere zum Ansteuern des Drehwerks eines Baggers
DE19620665 1996-05-22
PCT/EP1997/001920 WO1997044535A1 (fr) 1996-05-22 1997-04-17 Commande de mecanisme rotatif a systeme d'alimentation

Publications (2)

Publication Number Publication Date
EP0904467A1 true EP0904467A1 (fr) 1999-03-31
EP0904467B1 EP0904467B1 (fr) 2000-03-01

Family

ID=7795054

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97918141A Expired - Lifetime EP0904467B1 (fr) 1996-05-22 1997-04-17 Commande de mecanisme rotatif a systeme d'alimentation

Country Status (5)

Country Link
US (1) US6167702B1 (fr)
EP (1) EP0904467B1 (fr)
JP (1) JP2000510933A (fr)
DE (2) DE19620665C1 (fr)
WO (1) WO1997044535A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE19735111C2 (de) 1997-08-13 1999-06-02 Brueninghaus Hydromatik Gmbh Drehwerksteuerung mit Brems- und Steuerventilen
DE10000110B4 (de) * 2000-01-04 2004-06-24 Sauer-Sundstrand Gmbh & Co. Hydrostatischer Fahrzeugantrieb mit Steuerungseinrichtung und Steuerungseinrichtung für hydrostatische Antriebe
US6644335B2 (en) * 2000-12-15 2003-11-11 Caterpillar S.A.R.L. Precision orificing for pilot operated control valves
DE10110935C1 (de) * 2001-01-23 2002-11-28 Brueninghaus Hydromatik Gmbh Hydraulische Steuerung, insbesondere zum Ansteuern des Drehwerks eines Baggers
EP1225281B1 (fr) * 2001-01-23 2008-01-16 Brueninghaus Hydromatik Gmbh Commande hydraulique, notamment pour commander le mécanisme rotatif d'une excavatrice
DE10238614A1 (de) * 2002-08-17 2004-02-26 Claas Selbstfahrende Erntemaschinen Gmbh Ölvolumenausgleich im Ölkreislauf des hydraulischen Fahrantriebes einer selbstfahrenden Arbeitsmaschine
DE10331533B4 (de) * 2003-07-11 2005-11-03 Brueninghaus Hydromatik Gmbh Steuer- und Stellsystem für ein Hub- und Kippwerk eines Arbeitswerkzeugs in einer mobilen Arbeitsmaschine
DE102004033860B4 (de) * 2004-07-13 2014-02-13 Linde Hydraulics Gmbh & Co. Kg Hydraulische Steuerung, insbesondere Drehwerkssteuerung
US8661804B2 (en) 2009-12-11 2014-03-04 Caterpillar Inc. Control system for swashplate pump
DE102010001150A1 (de) * 2010-01-22 2011-07-28 Robert Bosch GmbH, 70469 Verfahren zum Steuern der Fördermenge einer Förderpumpe
DE102010020528B4 (de) * 2010-05-14 2023-05-17 Robert Bosch Gmbh Hydrostatischer Antrieb
US9611931B2 (en) * 2012-05-24 2017-04-04 GM Global Technology Operations LLC Method to detect loss of fluid or blockage in a hydraulic circuit using exponentially weighted moving average filter
WO2016025855A1 (fr) * 2014-08-15 2016-02-18 Eclipse, Inc. Brûleur à double sortie et procédé
KR102481767B1 (ko) 2015-03-10 2022-12-26 선더호프 엔지니어링 게엠베하 누출 손실을 보상하기 위한 방법 및 소정의 체적의 액체를 운반하기 위한 컨베이어 시스템
CN114537060A (zh) * 2020-11-24 2022-05-27 普瑞诺斯股份公司 用于准备滑雪道的履带式车辆和控制履带式车辆的绞盘的方法

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Also Published As

Publication number Publication date
JP2000510933A (ja) 2000-08-22
US6167702B1 (en) 2001-01-02
DE59701185D1 (de) 2000-04-06
DE19620665C1 (de) 1997-06-12
EP0904467B1 (fr) 2000-03-01
WO1997044535A1 (fr) 1997-11-27

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