EP0771949B1 - Verstellvorrichtung mit hydraulischer Zentriereinrichtung - Google Patents
Verstellvorrichtung mit hydraulischer Zentriereinrichtung Download PDFInfo
- Publication number
- EP0771949B1 EP0771949B1 EP96112820A EP96112820A EP0771949B1 EP 0771949 B1 EP0771949 B1 EP 0771949B1 EP 96112820 A EP96112820 A EP 96112820A EP 96112820 A EP96112820 A EP 96112820A EP 0771949 B1 EP0771949 B1 EP 0771949B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- control
- pressure
- piston
- actuating
- pressure chambers
- 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
Links
- 230000007935 neutral effect Effects 0.000 claims description 22
- 238000006073 displacement reaction Methods 0.000 claims description 17
- 230000002706 hydrostatic effect Effects 0.000 claims description 17
- 238000010586 diagram Methods 0.000 description 2
- 230000003213 activating effect Effects 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000007257 malfunction Effects 0.000 description 1
- 238000011144 upstream manufacturing Methods 0.000 description 1
Images
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
- F04B49/002—Hydraulic systems to change the pump delivery
-
- 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
- F04B49/10—Other safety measures
Definitions
- the invention relates to an adjusting device for adjusting one to the Displacement of a control piston acting on a hydrostatic machine.
- Such an adjustment device is e.g. known and includes from DE-OS 41 25 706 a spring-centered control device that the adjusting piston for adjusting the Displacement of the hydrostatic machine moves hydraulically.
- the control device is operated manually using a hand lever.
- a corresponding spring centering is provided.
- a control device for a radial piston machine goes from DE-OS 29 25 236 forth.
- the present invention is therefore based on the object of an adjusting device to adjust the displacement volume of a hydrostatic machine, in which the control piston is returned to its neutral position even in the event of a fault, in which the hydrostatic machine works without displacement, safely is guaranteed.
- the invention is based on the knowledge of an additional hydraulic To provide centering device that is only activated when both Control lines have no or insufficient control pressure.
- the solution according to the invention sees the combination of a switching valve with a Centering valve, the switching valve activating the centering valve when the Control pressure in both control pressure lines disappears. This relieves Centering valve with unequal pressures in the signal pressure chambers Signal pressure chamber to which the higher pressure is applied.
- the switching valve between the centering valve and one Pressure medium tank may be provided. It is only opened if the control lines do not have one or do not have sufficient control pressure, and then connects the centering valve to the pressure medium tank. To ensure that the switching valve is only opened if both control lines do not have sufficient control pressure, the switching valve a shuttle valve upstream according to claim 3, which the control line, the leads to higher control pressure, connects to the switching valve.
- the centering valve has a spring-centered centering piston on, between two centering pressure chambers connected to the signal pressure chambers is arranged.
- the centering piston is designed according to claim 5 so that it in a Neutral position, which the centering piston assumes when there is no pressure difference there is a connection between the signal pressure chambers Signal pressure chambers and the switching valve blocks.
- the connection between that signal pressure chamber that is subjected to the higher pressure with a pressure medium tank released if there is an imbalance between the There is pressure in the two signal pressure chambers.
- control device can be a feedback element have, which connects the actuating piston to the control piston to the control piston Adjustment of the adjusting piston in the direction of its neutral position. in the The feedback element then takes over centering during normal operation without malfunction. If the control device fails, e.g. by breaking the return spring, the -necessary centering and thus the swiveling back of the hydrostatic machine ensured by the hydraulic centering device.
- Fig. 1 shows a hydraulic circuit diagram of the adjustment device according to the invention for adjusting the control piston 3 arranged between the control pressure chambers 1 and 2.
- the displacement volume is not one shown hydrostatic machine changed, in which shown in Fig. 1 Neutral position the hydrostatic machine works without displacement.
- control pressure chambers 1, 2 are connected to a control device 8 via control pressure lines 6 and 7.
- the control device 8 serves to selectively apply the control pressure chambers 1, 2 and a predetermined control pressure in order to move the control piston 3 into a position corresponding to the displacement volume of the hydrostatic machine to be set.
- the control unit 8 is controlled via two control lines 9 and 10, which act on the control pressure chambers 11 and 12 of the control unit 8 with corresponding control pressures y 1 and y 2 .
- the control pressure chambers 11 and 12 are connected to the associated control lines 9 and 10 via corresponding connections 13 and 14. Between the control pressure chambers 11, 12, a control piston 16 is provided in the control unit 8, which is displaced as a function of the pressure difference between the control pressure chambers 11, 12 from a neutral position shown in FIG. 1 and one of the two control pressure lines 6 or 7 with this displacement connects the feed line 15, which leads the feed pressure p sp . As a result, the actuating pressure chamber 1 or 2 connected to the corresponding actuating pressure line 6 or 7 is acted upon by an appropriate actuating pressure, as a result of which the actuating piston 3 is moved into the desired position.
- a return device In order to cause the actuating piston 3 to be reset, a return device, generally designated 17, is provided.
- a return lever 18 engages in a corresponding groove in the actuating piston 3.
- the return lever 18 is operatively connected to the control piston 16, which will be described in more detail later with reference to FIGS. 2A and 2B.
- a restoring force proportional to the adjustment of the actuating piston 3 from its neutral position is exerted on the control piston 16, which counteracts the actuating force exerted on the control piston 16 by the control pressure y 1 or y 2 .
- the pressure in the actuating pressure chambers 1 and 2 does not continue to increase and the position of the actuating piston proportional to the control pressure y 1 or y 2 is reached.
- the arrangement described above also causes the actuating piston 3 to be returned to the neutral position shown in FIG. 1 via the reset device 17 described above if the control pressures y 1 and y 2 in the two control lines 9 and 10 are controlled to zero.
- a difficulty arises, however, when a fault occurs in the control device 8. In practice it has been shown that such a fault is often associated with a break in the return spring 20 of the return device 17. Since a break in the return spring 20 causes the actuating piston 3 to no longer be positively connected to the control piston 16, the return of the actuating piston 3 to its neutral position corresponding to the zero displacement volume of the hydrostatic machine is no longer guaranteed.
- the hydrostatic machine also works in the uncontrolled state, ie with control pressures y 1 and y 2 switched off, completely uncontrolled. Because of the now freely movable control piston 16 of the actuating piston 3 may be p sp assume any desired position and is also in the absence of supply pressure sp p in the feed line 15 due to the slow flowing actuating medium only slowly over the centering 4, 5 in the neutral position when still present feed pressure returned. In the meantime, the hydrostatic machine works with an uncontrolled displacement and can cause considerable damage.
- the hydraulic Centering device 21 comprises a centering valve 22 and a switching valve 23.
- Das Centering valve 22 has two exemplary embodiments shown in FIG. 1 Centering pressure chambers 24, 25, each with one of the signal pressure lines 6 and 7 are connected via centering lines 26 and 27. Between the centering chambers 24 and 25, a centering piston 28 is movably arranged.
- the centering piston 28 is in its Fig. 1 shown neutral position centered by centering springs 29, 30, at least one of the centering springs 29, 30 can be made adjustable. In the shown in Fig.
- the centering piston 28 has a central region, the Diameter is adapted to the surrounding cylinder and shown in Fig. 1 Neutral position blocks a connecting line 34, as well as two laterally arranged, tapered areas 32, 33.
- the tapered areas 32, 33 are each with one of the Centering lines 26 and 27 in connection.
- the central area 28 blocks the connection between the centering lines 26 and 27 with the connecting line 34 to the Switch valve 23. However, as soon as a between the centering lines 26 and 27 Adjusting the pressure difference, the centering piston 28 is laterally shifted accordingly, so that the centering line 26, 27, which carries the higher pressure, with the Connecting line 34 is connected.
- the switching valve 23 is in the embodiment shown in Fig. 1 between the Pressure medium tank 35 and the connecting line 34, which leads to the centering valve 21, arranged.
- the switching valve 23 comprises a movable against a return spring 36 Switching piston 37, which is acted upon by the pressure of a switching pressure chamber 38 and above a switching pressure which can be set by means of the return spring 36, the connection locks between the centering valve 21 and the pressure medium tank 35.
- the Switching pressure chamber 38 of the switching valve 23 is connected to the two via a shuttle valve 39 Control lines 9, 10 in connection.
- the shuttle valve 39 operates in such a way that each control line 9 or 10 carrying the higher pressure with the Switching pressure chamber 38 of the switching valve 23 is brought into connection.
- the operation of the hydraulic centering device according to the invention is as follows: As long as there is a predetermined minimum control pressure in at least one of the control lines 9 or 10, the hydraulic centering device 21 is not activated since the switching pressure chamber 38 of the switching valve 23 via the shuttle valve 39 with the higher of the two control pressures y 1 prevailing in the control lines 9 and 10 or y 2 is acted upon and thus shifts the switching piston 37 into a position in which the connection between the centering valve 22 and the pressure medium tank 35 is interrupted. However, as soon as the control lines 9 and 10 carry no or insufficient control pressure, the switching valve 23 is opened and the connecting line 34 is connected to the pressure medium tank 35.
- the signal pressure chamber 1 or 2 to which the higher signal pressure is applied becomes via the associated signal pressure line 6 or 7 and the corresponding centering line 26 or 27 Pressure medium tank 35 relieved. The relief takes place until a pressure equilibrium between the actuating pressures in the actuating pressure chambers 1 and 2 has been restored and thus the pressures guided by the centering lines 26 and 27 match and the centering piston 31 is returned to its neutral position.
- the hydraulic centering device 21 according to the invention described above brings about a swift and safe return of the adjusting piston 3 to its neutral position, in which the hydraulic machine works without displacement, even if a fault, in particular a break in the return spring 20, occurs in the control device 8.
- the arrangement also works reliably when the feed pressure p sp of the feed pressure line 15 is omitted, since the centering is effected by the centering springs 4, 5 after the control pressure chambers 1 and 2 are relieved.
- the hydraulic centering device 21 according to the invention which only requires a small amount of construction, prevents damage due to overloading of the otherwise uncontrolled working hydrostatic machine on the system.
- Control device 8 is briefly described with reference to FIGS. 2A and 2B.
- FIG. 2A shows a section through an exemplary embodiment of the control device 8.
- the control piston 16 is designed as a stepped piston and, when shifted from the neutral position shown in FIG. 2A, gives the connection between the ones shown in FIG. 1 at the control edges 50, 51 Signal pressure lines 6 and 7 with the feed line 15 free.
- the return lever 18 of the return device 17 already described is pivotally mounted about an axis 52.
- a pin 54 is formed on the extension 53 of the return lever 18, which pin deflects one of the two rocker arms 55 and 56 when the return lever 18 is pivoted .
- the return spring 20 is arranged between the hook-shaped end regions 57 and 58 of the rocker arms 55 and 56.
- the rocker arms 55 and 56 are in engagement with the control piston 16 in order to exert the restoring force already described with reference to FIG. 1.
- the return spring 20 effects the centering of the control piston 16 after switching off the control pressures y 1 and y 2 acting on the control piston 16 via the control pressure chambers 11 and 12.
- a break in the return spring 20, as already described, has the consequence that the centering of the control piston 16 and thus of the actuating piston 3 actuated by the latter is not guaranteed.
- the above-described hydraulic centering device 21 counteracts this disadvantage.
- the switching valve 23 can also be easily inserted into the centering lines 26 and 27 and interrupt the centering lines 26 and 27 when the control pressure y 1 and y 2 is present. It is also conceivable to switch the switching valve 23 by means of appropriate throttles instead of using a shuttle valve 39 Control pressure lines 9 and 10 to connect. Of course, the design of the centering valve 22 and the switching valve 23 can be varied while maintaining the function.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
Description
- Fig. 1
- einen hydraulischen Schaltplan eines Ausführungsbeispiels der erfindungsgemäßen Verstellvorrichtung,
- Fig. 2A
- einen Schnitt durch ein Ausführungsbeispiel einer Ansteuereinrichtung, die bei der Erfindung verwendet wird,
- Fig. 2B
- einen Schnitt entlang der Linie A-A in Fig. 2A.
Solange in zumindest einer der Steuerleitungen 9 oder 10 ein vorgegebener Mindest-Steuerdruck herrscht, ist die hydraulische Zentriereinrichtung 21 nicht aktiviert, da die Schaltdruckkammer 38 des Schaltventils 23 über das Wechselventil 39 mit dem höheren der beiden in den Steuerleitungen 9 und 10 herrschenden Steuerdrücke y1 oder y2 beaufschlagt ist und somit den Schaltkolben 37 in eine Position verschiebt, in der die Verbindung zwischen dem Zentrierventil 22 und dem Druckmitteltank 35 unterbrochen ist. Sobald die Steuerleitungen 9 und 10 jedoch keinen oder keinen ausreichenden Steuerdruck führen, wird das Schaltventil 23 geöffnet und die Verbindungsleitung 34 wird mit dem Druckmitteltank 35 verbunden. Sofern bei Aktivierung des Zentrierventils 22 ein Ungleichgewicht zwischen den Drücken in den beiden Stelldruckkammern 1 und 2 herrscht, wird diejenige Stelldruckkammer 1 oder 2, welche mit dem höheren Stelldruck beaufschlagt ist, über die zugeordnete Stelldruckleitung 6 oder 7 und die entsprechende Zentrierleitung 26 oder 27 zum Druckmitteltank 35 hin entlastet. Die Entlastung erfolgt so lange, bis sich ein Druckgleichgewicht zwischen den Stelldrücken in den Stelldruckkammern 1 und 2 wieder eingestellt hat und somit auch die von den Zentrierleitungen 26 und 27 geführten Drücke übereinstimmen und der Zentrierkolben 31 in seine Neutralstellung zurückgeführt ist.
Claims (6)
- Verstell-Vorrichtung zum Verstellen eines zwischen zwei Stelldruckkammern (1, 2) angeordneten, auf das Verdrängungsvolumen einer hydrostatischen Maschine einwirkenden Stellkolbens (3) mit
einer Ansteuereinrichtung (8),
die zwei mit je einer Steuerleitung (9, 1O) verbundene Steuerdruckkammern (11, 12) und einen zwischen den Steuerdruckkammern (11, 12) angeordneten Steuerkolben (16) aufweist, der in Abhängigkeit von der Druckdifferenz zwischen den Steuerdruckkammern (11, 12) aus einer Neutralstellung verschoben wird und dadurch eine der Stelldruckkammern (1, 2) mit einer Speisedruckleitung (15) verbindet,
und mit einer hydraulischen Zentriereinrichtung (21),
die ein mit den Steuerleitungen (9, 1o) verbundenes Schaltventil (23) und ein mit den Stelldruckkammern (1, 2) verbundenes Zentrierventil (22) aufweist, wobei das Schaltventil (23) bei verschwindendem Steuerdruck in beiden Steuerleitungen (9, 1o) das Zentrierventil (22) so schaltet, daß dieses bei einer Druckdifferenz zwischen den Stelldruckkammern (1, 2) die mit höherem Druck beaufschlagte Stelldruckkammer (1, 2) entlastet, um den Stellkolben (3) in seine Neutralstellung, in der die hydrostatische Maschine ohne Verdrängungsvolumen arbeitet, zurückzuführen. - Verstell-Vorrichtung nach Anspruch 1,
dadurch gekennzeichnet,
daß das Schaltventil (23) zwischen dem Zentrierventil (22) und einem Druckmitteltank (35) angeordnet und nur geöffnet ist, wenn die Steuerleitungen (9, 1O) keinen oder keinen ausreichenden Steuerdruck führen. - Verstell-Vorrichtung nach Anspruch 1 oder 2,
dadurch gekennzeichnet,
daß ein mit beiden Steuerleitungen (9, 10) und dem Schaltventil (23) verbundenes Wechselventil (39) vorgesehen ist, das die den höheren Steuerdruck führende Steuerleitung (9, 10) mit dem Schaltventil (23) verbindet. - Verstell-Vorrichtung nach einem der Ansprüche 1 bis 3,
dadurch gekennzeichnet,
daß das Zentrierventil (22) einen federzentrierten Zentrierkolben (28) aufweist, der zwischen zwei mit jeweils einer der Stelldruckkammern (1, 2) verbundenen Zentrierdruckkammern (24, 25) angeordnet ist. - Verstell-Vorrichtung nach Anspruch 2 und 4,
dadurch gekennzeichnet,
daß der Zentrierkolben (28) so ausgebildet ist, daß er in seiner Neutralstellung, in der keine Druckdifferenz zwischen den Zentrierdruckkammern (24, 25) herrscht, die Verbindung zwischen den Stelldruckkammern (1, 2) und dem Schaltventil (23) sperrt und bei Verschiebung aus der Neutralstellung durch eine Druckdifferenz zwischen den Zentrierdruckkammern (24, 25) die Verbindung der mit dem höheren Druck beaufschlagten Stelldruckkammer (1, 2) über das Schaltventil (23) zum Druckmitteltank (35) hin freigibt. - Verstell-Vorrichtung nach einem der Ansprüche 1 bis 5,
dadurch gekennzeichnet,
daß die Ansteuereinrichtung (8) ein Rückführelement (17) aufweist, das den Stellkolben (3) mit dem Steuerkolben (16) verbindet, um den Steuerkolben (16) nach Verstellen des Stellkolbens (3) in Richtung auf seine Neutralstellung zurückzuführen.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19540654 | 1995-10-31 | ||
DE19540654A DE19540654C1 (de) | 1995-10-31 | 1995-10-31 | Verstellvorrichtung mit hydraulischer Zentriereinrichtung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0771949A1 EP0771949A1 (de) | 1997-05-07 |
EP0771949B1 true EP0771949B1 (de) | 2001-05-09 |
Family
ID=7776329
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96112820A Expired - Lifetime EP0771949B1 (de) | 1995-10-31 | 1996-08-08 | Verstellvorrichtung mit hydraulischer Zentriereinrichtung |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0771949B1 (de) |
DE (2) | DE19540654C1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102022210332A1 (de) | 2022-09-29 | 2024-04-04 | Robert Bosch Gesellschaft mit beschränkter Haftung | Hebelvorrichtung mit geklemmter Hebelachse |
Families Citing this family (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE10006405B4 (de) * | 2000-02-14 | 2005-04-14 | Brueninghaus Hydromatik Gmbh | Verstellvorrichtung |
DE10063526C1 (de) * | 2000-12-20 | 2002-07-11 | Brueninghaus Hydromatik Gmbh | Verstellvorrichtung zum Verstellen eines auf das Verdrängungsvolumen einer hydrostatischen Maschine einwirkenden Stellkolbens |
DE10063525B4 (de) * | 2000-12-20 | 2005-07-07 | Brueninghaus Hydromatik Gmbh | Verstellvorrichtung zum Verstellen eines auf das Verdrängungsvolumen einer hydrostatischen Maschine einwirkenden Stellkolbens |
DE10220376B4 (de) * | 2002-05-07 | 2004-07-15 | Brueninghaus Hydromatik Gmbh | Hydraulische Steuerung mit aktiver Rückstellung |
DE10220889C5 (de) * | 2002-05-10 | 2009-05-28 | Brueninghaus Hydromatik Gmbh | Verstellvorrichtung für hydrostatische Kolbenmaschinen |
DE102005037619B4 (de) | 2005-08-09 | 2020-07-09 | Brueninghaus Hydromatik Gmbh | Regelventileinheit mit Wechselanschlag |
DE102005037620A1 (de) | 2005-08-09 | 2007-02-15 | Brueninghaus Hydromatik Gmbh | Regelvorrichtung für eine hydrostatische Kolbenmaschine mit elektronischer Steuereinheit |
DE102007016293B3 (de) * | 2007-04-04 | 2008-10-02 | Sauer-Danfoss Gmbh & Co Ohg | Verstelleinheit für eine Axialkolbenmaschine |
EP2138720A3 (de) | 2008-06-24 | 2010-01-20 | MALI Holding AG | Verstellvorrichtung für die Verstellung von Axialkolbenmaschinen. |
DE102008049633A1 (de) | 2008-09-30 | 2010-04-01 | Robert Bosch Gmbh | Stellvorrichtung für eine hydrostatische Maschine mit verbesserter Rückstellung |
DE102008052419A1 (de) * | 2008-10-21 | 2010-04-22 | Sauer-Danfoss Gmbh & Co Ohg | Axialkolbenmaschine mit Verstelleinrichtung des Fördervolumens |
DE102010006988A1 (de) | 2010-01-05 | 2011-07-07 | Robert Bosch GmbH, 70469 | Verstellvorrichtung für eine hydrostatische Kolbenmaschine |
DE102010045540A1 (de) | 2010-09-15 | 2012-03-15 | Robert Bosch Gmbh | Schwenkwinkelsensor |
DE102011112215A1 (de) | 2011-09-02 | 2013-03-07 | Robert Bosch Gmbh | Spannhebelanordnung, Verfahren zum Herstellen eines Spannhebels und Ansteuergerät |
DE102011115667A1 (de) | 2011-09-29 | 2013-04-04 | Robert Bosch Gmbh | Ansteuergerät und Verfahren zur Montage eines Ansteuergeräts |
DE102011121520A1 (de) | 2011-12-16 | 2013-06-20 | Robert Bosch Gmbh | Verstelleinrichtung für eine Axialkolbenmaschine undAxialkolbenmaschine mit einer Verstelleinrichtung |
DE102012214619A1 (de) * | 2012-08-17 | 2014-02-20 | Robert Bosch Gmbh | Aktoreinrichtung und Axialkolbenmaschine |
DE102013110568A1 (de) * | 2013-09-24 | 2015-03-26 | Claas Selbstfahrende Erntemaschinen Gmbh | Antriebssystem für hydraulisch angetriebene Arbeitsorgane einer Arbeitsmaschine |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3429225A (en) * | 1966-06-09 | 1969-02-25 | Abex Corp | Electrohydraulic displacement control with mechanical feedback |
DE2913534A1 (de) * | 1979-04-04 | 1980-10-16 | Bosch Gmbh Robert | Einrichtung zur regelung des foerderstroms und zur begrenzung des foerderdrucks einer verstellbaren pumpe |
DE2925236A1 (de) * | 1979-06-22 | 1981-01-15 | Danfoss As | Steuergeraet fuer eine pumpe mit verstellbarer foerdermenge |
DE3232695C2 (de) * | 1982-09-02 | 1984-08-16 | Hydromatik GmbH, 7915 Elchingen | Leistungsregel-Vorrichtung für eine Hydropumpe |
JPH0751947B2 (ja) * | 1985-01-18 | 1995-06-05 | 石炭露天掘機械技術研究組合 | 液圧閉回路に介在された液圧ポンプの制御装置 |
DE3600787C1 (de) * | 1986-01-14 | 1987-04-02 | Danfoss As | Steuergeraet fuer eine Pumpe mit einstellbarer Foerdermenge |
DE3709504C2 (de) * | 1987-03-23 | 1995-02-02 | Rexroth Mannesmann Gmbh | Ventileinrichtung |
DE4125706C1 (de) * | 1991-08-02 | 1993-01-14 | Hydromatik Gmbh, 7915 Elchingen, De |
-
1995
- 1995-10-31 DE DE19540654A patent/DE19540654C1/de not_active Expired - Fee Related
-
1996
- 1996-08-08 EP EP96112820A patent/EP0771949B1/de not_active Expired - Lifetime
- 1996-08-08 DE DE59606872T patent/DE59606872D1/de not_active Expired - Lifetime
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102022210332A1 (de) | 2022-09-29 | 2024-04-04 | Robert Bosch Gesellschaft mit beschränkter Haftung | Hebelvorrichtung mit geklemmter Hebelachse |
Also Published As
Publication number | Publication date |
---|---|
DE19540654C1 (de) | 1996-12-19 |
DE59606872D1 (de) | 2001-06-13 |
EP0771949A1 (de) | 1997-05-07 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP0771949B1 (de) | Verstellvorrichtung mit hydraulischer Zentriereinrichtung | |
DE2752087C2 (de) | ||
DE2350390C3 (de) | ||
DE2547912B2 (de) | Hydraulischer Unterbrecher | |
DE3709504C2 (de) | Ventileinrichtung | |
DE4342642C2 (de) | Elektro-hydraulische Schnellfallschaltung | |
DE2319726C3 (de) | Lastabhängig arbeitende Bremsdrucksteuereinrichtung für ein druckmittelbetätigbares Fahrzeug-Bremssystem | |
EP2138720A2 (de) | Verstellvorrichtung für die Verstellung von Axialkolbenmaschinen. | |
DE19608801A1 (de) | Hydraulisches Lasthalte- bzw. Senkbremsventil | |
DE69029904T2 (de) | Hydraulische schaltungsanordnung | |
DE3225132A1 (de) | Hydraulisches sicherheitsbremsventil | |
EP0932783B1 (de) | Kombiniertes druckminder- und schaltventil | |
DE2741809B2 (de) | Bremskraftregler für eine Hydraulikbremsanlage | |
DE69703170T2 (de) | Hydrauliksystem | |
DE3006530A1 (de) | Hydraulisches blockier- oder halteventil | |
DE3635625A1 (de) | Vorsteuergeraet | |
DE3447380C2 (de) | ||
DE3046703A1 (de) | Druckmittelbetaetigte fernsteuerung | |
DE2947842C2 (de) | Hydraulische Sicherheitssteuerung mit Druckstufenregelventil | |
DE68910505T2 (de) | Schnüffelventilanordnung. | |
EP0158738A2 (de) | Hydraulische Überlastungsschutzvorrichtung für einen Ladekran | |
AT407369B (de) | Einrichtung zum umstellen der beweglichen teile von schienenweichen oder -kreuzungen | |
DE1460706C3 (de) | Hydraulische Drucksteuerung für Kalanderwalzen o.dgl | |
DE2519973B2 (de) | Entlastungsventil | |
EP0073887A2 (de) | Hydraulisches Steuergerät |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): DE FR GB IT SE |
|
17P | Request for examination filed |
Effective date: 19970602 |
|
GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
17Q | First examination report despatched |
Effective date: 20000906 |
|
GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): DE FR GB IT SE |
|
GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) |
Effective date: 20010509 |
|
ITF | It: translation for a ep patent filed | ||
REF | Corresponds to: |
Ref document number: 59606872 Country of ref document: DE Date of ref document: 20010613 |
|
ET | Fr: translation filed | ||
REG | Reference to a national code |
Ref country code: GB Ref legal event code: IF02 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
26N | No opposition filed | ||
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20090819 Year of fee payment: 14 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: SE Payment date: 20090821 Year of fee payment: 14 Ref country code: GB Payment date: 20090821 Year of fee payment: 14 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20091026 Year of fee payment: 14 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20090825 Year of fee payment: 14 |
|
EUG | Se: european patent has lapsed | ||
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20100808 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20110502 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100808 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 59606872 Country of ref document: DE Effective date: 20110301 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100831 Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20110301 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100808 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20100809 |