EP1188934A2 - Steuerungsvorrichtung für einen hydraulischen Volumenstrom - Google Patents
Steuerungsvorrichtung für einen hydraulischen Volumenstrom Download PDFInfo
- Publication number
- EP1188934A2 EP1188934A2 EP01121812A EP01121812A EP1188934A2 EP 1188934 A2 EP1188934 A2 EP 1188934A2 EP 01121812 A EP01121812 A EP 01121812A EP 01121812 A EP01121812 A EP 01121812A EP 1188934 A2 EP1188934 A2 EP 1188934A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- hydraulic
- reducing valve
- control device
- pressure reducing
- pressure
- 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.)
- Withdrawn
Links
Images
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
- F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
- F15B21/14—Energy-recuperation means
-
- 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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/003—Systems with load-holding valves
-
- 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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
- F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
Definitions
- the invention relates to a control device for a volume flow flowing in a hydraulic system Hydraulic medium according to the preamble of claim 1.
- a generic control device for lowering is known a load on a hydraulic cylinder.
- the Hydraulic cylinder via a check valve and a hydraulic motor connected to a hydraulic fluid tank.
- the hydraulic motor is driven by the pressure of the hydraulic fluid driven.
- the hydraulic pump is mostly by one Electric motor driven.
- When lowering a load the electric motor is driven by the hydraulic motor and works in this operating state generator in the third quadrant.
- the lowering capacity exceeds the lifting capacity in lifting operation clear.
- the electric motor must therefore take up power be dimensioned larger than this in lowering operation would be necessary for pure lifting operation. This has higher costs disadvantageous for larger electric motors and requires above also a larger installation space.
- the invention relates to a control device for a volume flow flowing in a hydraulic system Hydraulic fluid of at least one loaded working fluid, especially for lifting and lowering a load, with at least a check valve and at least one hydraulic motor.
- a pressure reducing valve so is arranged that when lowering the load on the hydraulic motor pending pressure is reduced.
- the pressure reducing valve increases high loads or high pressures in the hydraulic system, part of the hydrostatic energy of the work equipment on, the essentially of the potential Energy corresponds to the load when lowering it. That energy is partly due to the pressure reduction when flowing through of the hydraulic fluid through the pressure reducing valve converted into heat by internal friction.
- the heat output corresponds to the product of flow rate and pressure difference on the pressure reducing valve.
- the power consumption of the hydraulic motor and thus that of a generator driven by it working electric motor decreases accordingly Heat output. It can therefore be a smaller one Electric motor used and there can be thermal relief can be achieved. This leads to a cost reduction.
- the smaller design of the electric motor still leads to a Space reduction.
- this Pressure reducing valve biased in the opening direction Slider on through the outlet side of the pressure reducing valve hydraulic fluid under reduced pressure in Closing direction is displaceable.
- the slider overcomes the Preload in the opening direction and closes the pressure reducing valve.
- the opening cross section of the pressure reducing valve increases and the pressure difference at the pressure reducing valve increases. at constant inlet pressure, therefore, the outlet pressure decreases.
- the force on the slide in the closing direction decreases, and the pressure reducing valve opens again.
- the output side depends Pressure on the pressure reducing valve from the preload from.
- the design of the pressure reducing valve as a slide valve is characterized by a simple structure and reliability out.
- the slide is preferably in the opening direction and in Closing direction with surfaces that differ in size Hydraulic fluid can be applied.
- Differential surface principle built pressure reducing valve offers the advantage of a weaker dimensionable biasing element.
- a spring can be used who need a smaller installation space, because the in Direction of opening of the pressure reducing valve thus supports the preload.
- the resulting total force results from the pressure of the hydraulic medium multiplied with the difference of the two areas.
- the slide advantageously has the shape of a sleeve on, which is closed on one axial end face and on the other is open to drain hydraulic fluid.
- the Sleeve is slidable in a housing of the pressure reducing valve. In its outer surface it has at least one radial one Opening as hydraulic fluid inlet on that with a hydraulic medium supply channel in the housing of the pressure reducing valve Regulation of the reduced pressure of the hydraulic fluid in changeable Extent can be brought into overlap. By size The hydraulic fluid flow rate becomes the cover area and thus regulates the pressure reduction. The larger the cross section the overlap between the opening in the sleeve and the opening of the hydraulic medium supply channel, the larger is the hydraulic fluid flow and the smaller it is the pressure drop at this point.
- the sleeve can also have several radial Have openings that connect to the hydraulic fluid supply channel connected annular, enclosing the sleeve Groove on the inside of the housing to cover can be brought.
- a spring preferably exerts a spring acting in the opening direction Force on the sleeve, the pressure force of the hydraulic fluid on an inner surface of a closed face of the Counteracts sleeve. In this way, the bias of the Slider against the hydraulic force in the simplest way be designed.
- a Part of the outer surface of the closed face of the sleeve for partial compensation of the closed on the inner surface Frontal pressure force also with hydraulic fluid applied.
- the pressure force on this part of the outer surface acts in the opening direction of the pressure reducing valve and thus supports the preload.
- the resulting total force results from the pressure of the hydraulic medium multiplied with the difference between the inner surface and the outer Part of the face of the sleeve.
- the closed end face preferably has a hydraulic medium duct for hydraulic fluid loading part of the outer surface of the closed face of the Sleeve on.
- This hydraulic fluid loading can be done in the simplest Way be designed as a hole and is very inexpensive.
- the pressure reducing valve is advantageously by means of a Leakage line connected to a hydraulic fluid tank. Hydraulic fluid, that through a seal from a press pressurized valve chamber of the pressure reducing valve into one depressurized part of the pressure reducing valve, such as a spring chamber that emerges is in via this leakage line the hydraulic fluid tank can be removed. In this way, a Leakage loss from hydraulic fluids can be avoided, the environment spared and in particular an undesirable pressure build-up be avoided in a depressurized room.
- a check valve is preferably parallel to the pressure reducing valve connected. This check valve forms in Lift operation of the work equipment or a bypass for the Hydraulic fluid. This can be beneficial in the event of a regulated hydraulic pump the work equipment hydraulic fluid can be applied quickly and easily.
- FIG. 1 is a schematic diagram of an inventive Control device shown.
- a working cylinder 12 will to the piston stroke to lift a load from a hydraulic pump 10 supplied with hydraulic fluid from a hydraulic fluid tank 14.
- the hydraulic pump 10 is preferably used by one in both Directions driven variable speed electric motor 16.
- the lowering of the piston in the working cylinder 12 for lowering the load is controlled by a check valve 18. Should the load is held, the check valve 18 is closed. It is opened to lower the load. hydraulic fluid flows through the check valve 18 and the hydraulic pump 10 to the hydraulic fluid tank 14.
- the hydraulic pump 10 runs backwards in the mode of action of a hydraulic motor 20 and drives the electric motor 16.
- the electric motor 16 works in this operating state generator in the third quadrant.
- the hydraulic fluid pressure is the weight of the Load determined. At high loads or high pressures in the Hydraulic fluid, the lowering capacity could increase the lifting capacity significantly exceed.
- the pressure reducing valve 22 is shown in detail in FIG. 2.
- the pressure reducing valve 22 has one in the opening direction 28 by means of a spring 30 preloaded slide 32, the through the output side of the pressure reducing valve 22 below reduced pressure hydraulic fluid in the closing direction 34 is displaceable.
- the slider 32 has the shape a sleeve 36, which is closed on one axial end face 38 and on the other to drain hydraulic fluid is open. This sleeve 36 is in a housing 40 of the Pressure reducing valve 22 slidable.
- the sleeve 36 has in her Shell surface 42 two radial openings 44, 46 in the form of Bores as hydraulic fluid inlet, which with an annular, the groove 36 comprising the sleeve 36 on the inside of the housing 40 can be brought to cover.
- the annular groove 48 is with a hydraulic fluid supply channel 50 connected in the housing 40 of the pressure reducing valve 22.
- the spring 30 exerts a force acting in the opening direction 28 on the sleeve 36, the pressure force of the hydraulic fluid counteracts the inner surface 52 of the closed end face 38. With increasing pressure in the sleeve 36, the Force on the inner surface 52 of the closed face 38. The sleeve 36 is thus counteracted in the illustration according to FIG. 2 the spring force increasingly shifted to the left.
- the coverage cross section between the radial openings 44, 46 and the groove 48 comprising the sleeve 36 or the hydraulic medium supply channel 50 decreases. The coverage cross section determines the inlet cross-section of the pressure reducing valve 22.
- An end stop 68 prevents the sleeve 36 by the force of the spring 30 so far in the opening direction 28 is shifted from the stable regulatory equilibrium into an unstable equilibrium that with increasing displacement of the sleeve 36 in the opening direction 28 the overlap cross section between the radial Openings 44, 46 and the groove 48 or sleeve 36 of the hydraulic medium supply channel 50 decreases again.
- the closed end face 38 of the sleeve 36 has a bore as hydraulic medium bushing 54. This hole connects the interior 58 of the sleeve 36 with an annular space 60 between the housing 40 and the end face 38 of the sleeve 36. In this annulus 60 there is the same pressure as in Interior 58 of the sleeve 36.
- the annular space 60 encloses one cylindrical extension 62 of the end face 38 of the sleeve 36, which extends into a bore 64 of the housing 40.
- the the extension 62 of the end face 38 as an annular surface Part of the outer surface 56 of the closed end 38 becomes thus also acted upon by hydraulic fluid pressure. On Part of the closed face on the inner surface 52 38 acting pressure force is compensated in this way.
- the Pressure force on this part of the outer surface 56 acts in the opening direction 28 of the pressure reducing valve 22 and supported thus the preload of the spring 30.
- the resulting total force results from the pressure of the hydraulic medium multiplied with the difference between the inner surface 52 and the outer Partial surface of the end face 38 of the sleeve 36. This corresponds the product of the pressure and the cross-sectional area of the extension 62 of the end face 38.
- This after this so-called Differential surface principle built pressure reducing valve 22 has the advantage that the spring 30 is dimensioned weaker can be. Otherwise, the spring would be 30 significantly larger installation space required.
- the bore 64 of the housing 40, in which the cylindrical Extension 62 of the end face 38 of the sleeve 36 extends, and in which the spring 30 is received, is by means of a Leakage line 66 connected to the hydraulic fluid tank 14. Hydraulic fluid through a seal, not shown from the pressurized annulus 60 of the pressure reducing valve 22 in the unpressurized space of the bore 64 of the pressure reducing valve 22 emerges, is via this leakage line 66 discharged into the hydraulic fluid tank 14.
- the level of the pressure at the hydraulic motor 20 is determined by the bias of the spring 30 is set.
- the pressure is allowed should not be chosen too small, otherwise in the generator Operation of the electric motor 16 of the hydraulic motor 20 no longer starts and thus the volume flow of the hydraulic medium is interrupted is.
Abstract
Description
- Fig. 1
- ein Prinzipschaltbild einer erfindungsgemäßen Steuervorrichtung und
- Fig. 2
- ein Druckminderventil im geöffneten Zustand.
Claims (11)
- Steuerungsvorrichtung für einen in einem Hydrauliksystem fließenden Volumenstrom eines Hydraulikmittels zumindest eines belasteten Arbeitsmittels (12), insbesondere zum Heben und Senken einer Last, mit zumindest einem Sperrventil (18) und zumindest einem Hydromotor (20), dadurch gekennzeichnet, daß in dem Hydrauliksystem zwischen dem Arbeitsmittel (12) and dem Hydromotor (20) ein Druckminderventil (22) so angeordnet ist, daß es beim Senken der Last den am Hydromotor (20) anstehenden Druck verringert.
- Steuerungsvorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß das Druckminderventil (22) einen in Öffnungsrichtung (28) vorgespannten Schieber (32) aufweist, der durch das ausgangsseitig des Druckminderventils (22) unter geminderten Druck stehenden Hydraulikmittel in Schließrichtung (34) verschiebbar ist.
- Steuerungsvorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß der Schieber (32) in Öffnungsrichtung (28) und in Schließrichtung (34) über von der Größe differierende Flächen (56, 52) mit Hydraulikmittel beaufschlagbar ist.
- Steuerungsvorrichtung nach Anspruch 2 oder 3, dadurch gekennzeichnet, daß der Schieber (32) die Form einer Hülse (36) aufweist, die auf der einen axialen Stirnseite (38) geschlossen ist und auf der anderen zum Ablauf des Hydraulikmittels offen ist, und daß die Hülse (36) in einem Gehäuse (40) des Druckminderventils (22) verschiebbar ist und in ihrer Mantelfläche (42) mindestens eine radiale Öffnung (44, 46) als Hydraulikmittelzulauf aufweist, die mit einem Hydraulikmittelzufuhrkanal (50) im Gehäuse (40) des Druckminderventils (22) zur Regelung des geminderten Drucks des Hydraulikmittels in veränderbarem Ausmaß in Überdeckung bringbar ist.
- Steuerungsvorrichtung nach Anspruch 4, dadurch gekennzeichnet, daß eine Feder (30) eine in Öffnungsrichtung (28) wirkende Kraft auf die Hülse (36) ausübt, die der Druckkraft des Hydraulikmittels auf eine Innenfläche (52) einer geschlossenen Stirnseite (38) der Hülse (36) entgegenwirkt.
- Steuerungsvorrichtung nach Anspruch 3 und 5, dadurch gekennzeichnet, daß ein Teil der Außenfläche (56) der geschlossenen Stirnseite (38) der Hülse (36) zur Teilkompensation der auf die Innenfläche (52) der geschlossenen Stirnseite (38) wirkenden Druckkraft ebenfalls mit Hydraulikmittel beaufschlagt wird.
- Steuerungsvorrichtung nach Anspruch 6, dadurch gekennzeichnet, daß die geschlossene Stirnseite (38) eine Hydraulikmitteldurchführung (54) zur Hydraulikmittelbeaufschlagung eines Teils der Außenfläche (56) der geschlossenen Stirnseite (38) der Hülse (36) aufweist.
- Steuerungsvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß das Druckminderventil (22) mittels einer Leckageleitung (66) mit einem Hydraulikmitteltank (14) verbunden ist, über die aus dem Druckminderventil (22) durch eine Dichtung austretendes Hydraulikmittel in den Hydraulikmitteltank (14) abführbar ist.
- Steuerungsvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß ein Rückschlagventil (26) parallel zum Druckminderventil (22) geschaltet ist, das im Hubbetrieb des oder der Arbeitsmittel (12) einen Bypass (24) für das Hydraulikmittel ausbildet.
- Steuervorrichtung nach Anspruch 9, dadurch gekennzeichnet, daß das Rückschlagventil (26) parallel zum Sperrventil (18) geschaltete ist, das in Reihe zum Druckminderventil (22) liegt.
- Steuerungsvorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Hydromotor (20) im Hubbetrieb des oder der Arbeitsmittel (12) als Hydropumpe (10) arbeitet.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE2000145213 DE10045213A1 (de) | 2000-09-13 | 2000-09-13 | Steuerungsvorrichtung für einen hydraulischen Volumenstrom |
DE10045213 | 2000-09-13 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1188934A2 true EP1188934A2 (de) | 2002-03-20 |
EP1188934A3 EP1188934A3 (de) | 2004-01-21 |
Family
ID=7656011
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP01121812A Withdrawn EP1188934A3 (de) | 2000-09-13 | 2001-09-11 | Steuerungsvorrichtung für einen hydraulischen Volumenstrom |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP1188934A3 (de) |
DE (1) | DE10045213A1 (de) |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1369377A3 (de) * | 2002-06-05 | 2006-07-05 | BT Industries | Verfahren zur Steuerung eines Hubwagens |
EP1628020A3 (de) * | 2004-08-17 | 2008-09-03 | Jungheinrich Aktiengesellschaft | Fluidschaltung und Flurförderzeug mit Fluidschaltung |
DE102007027567B4 (de) | 2007-06-15 | 2018-03-01 | Robert Bosch Gmbh | Steueranordnung mit Rohrbruchsicherungsfunktion |
US11009048B1 (en) | 2020-09-09 | 2021-05-18 | Robert Bosch Gmbh | Boom lift system |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2493111A (en) * | 1945-02-01 | 1950-01-03 | Weatherhead Co | Pressure regulator |
US2594626A (en) * | 1946-09-09 | 1952-04-29 | Clarence E Earle | Safety valve |
CH405851A (de) * | 1963-11-27 | 1966-01-15 | Gunzenhauser Ag J & R | Druckreduzierventil |
DE2618046A1 (de) * | 1976-04-24 | 1977-11-10 | Sven O I Jonsson | Verfahren und vorrichtung zur ausnutzung gespeicherter potentieller energie beim entladen von waren |
SU735560A1 (ru) * | 1978-09-19 | 1980-05-25 | Горьковский Институт Инженеров Водного Транспорта | Электрогидравлический привод напольного грузоподъемного средства |
AU7232781A (en) * | 1981-02-13 | 1982-08-19 | Groh West Pty. Ltd. | Dual circuit pressure equalising valve |
JPS6068410A (ja) * | 1983-09-22 | 1985-04-19 | Nachi Fujikoshi Corp | 逆流可能レデュ−シングバルブ |
JP2628397B2 (ja) * | 1990-04-25 | 1997-07-09 | 回生工業株式会社 | インバータ電源を用いた油圧エレベータの速度制御方法 |
DE4140408A1 (de) * | 1991-12-07 | 1993-06-09 | Robert Bosch Gmbh, 7000 Stuttgart, De | Elektrohydraulische steuereinrichtung |
JP3376263B2 (ja) * | 1997-12-05 | 2003-02-10 | 株式会社豊田自動織機 | バッテリ式産業車両における油圧装置 |
-
2000
- 2000-09-13 DE DE2000145213 patent/DE10045213A1/de not_active Withdrawn
-
2001
- 2001-09-11 EP EP01121812A patent/EP1188934A3/de not_active Withdrawn
Non-Patent Citations (1)
Title |
---|
None |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1369377A3 (de) * | 2002-06-05 | 2006-07-05 | BT Industries | Verfahren zur Steuerung eines Hubwagens |
EP1628020A3 (de) * | 2004-08-17 | 2008-09-03 | Jungheinrich Aktiengesellschaft | Fluidschaltung und Flurförderzeug mit Fluidschaltung |
DE102007027567B4 (de) | 2007-06-15 | 2018-03-01 | Robert Bosch Gmbh | Steueranordnung mit Rohrbruchsicherungsfunktion |
US11009048B1 (en) | 2020-09-09 | 2021-05-18 | Robert Bosch Gmbh | Boom lift system |
Also Published As
Publication number | Publication date |
---|---|
EP1188934A3 (de) | 2004-01-21 |
DE10045213A1 (de) | 2002-03-28 |
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