EP0939225A2 - Leistungsregeleinrichtung für mehrere verstellbare Hydropumpen - Google Patents
Leistungsregeleinrichtung für mehrere verstellbare Hydropumpen Download PDFInfo
- Publication number
- EP0939225A2 EP0939225A2 EP99103324A EP99103324A EP0939225A2 EP 0939225 A2 EP0939225 A2 EP 0939225A2 EP 99103324 A EP99103324 A EP 99103324A EP 99103324 A EP99103324 A EP 99103324A EP 0939225 A2 EP0939225 A2 EP 0939225A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- control pressure
- power control
- line
- control device
- working
- 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
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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
- F04B49/08—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
- F04B2205/00—Fluid parameters
- F04B2205/16—Opening or closing of a valve in a circuit
Definitions
- the invention relates to a power control device for limiting the power at least a first and a second connected to the power control device, adjustable hydraulic pump.
- a power control device is e.g. from the EP 0 133 870 A1 known.
- a power control device is included described a hyperbola controller, which is located directly on the adjusting device of the hydraulic pump attacks.
- the known power control device also for controlling two synchronously operating hydraulic pumps are used that promote in different work lines.
- the Hyperbola controller includes a pivot lever on which an engagement element in the form of a control slide inserted into the adjusting piston of the adjusting device.
- the Control spool is via a bore provided in the control piston with the Signal pressure chamber connected, which in turn via a diaphragm seal to the two Working lines of the hydraulic pumps is connected.
- the signal pressure chamber is therefore with the average working pressure of the two hydraulic pumps.
- the middle one Working pressure also engages through the bore provided in the actuating piston Control spool in a direction perpendicular to the direction of displacement of the actuating piston and thus acts on the swivel lever.
- the lever arm over which the as Attack element serving control slide on the pivot lever depends on the Position of the actuating piston and thus of that set by the adjusting device Displacement volume of the two synchronously operating hydraulic pumps. That about that Torque lever attacking torque is therefore the product of the averaged Working pressure of the two working pressure lines and the same for both hydraulic pumps Funding volume proportional. This product of working pressure and delivery volume corresponds to the power output by the hydraulic pumps.
- hyperbola controller can therefore be implemented a power control device that has an exact Power limitation to a predetermined maximum power enabled.
- the default Maximum power has in a diagram, in which the working pressure as a function of Delivery volume is shown (p-V diagram) in the form of a hyperbola.
- EP 0 133 870 A1 also addresses the maximum power to which the Power control device regulates the two synchronously working hydraulic pumps, from the working pressure of a third hydraulic pump can depend on with high power output this third hydraulic pump to avoid overloading the overall system.
- the object is in connection with the characterizing features of claim 1 solved with the generic features.
- the invention is based on the concept of the hyperbolic regulator with the swivel lever in to integrate a structurally separate unit from the hydraulic pump.
- the swivel lever is not over the attack element with the adjusting piston of the adjusting device Hydraulic pump connected. Instead, it affects the pivot position of the pivot lever of the hyperbolic regulator, a control pressure valve that controls the control pressure for the adjustment devices of the connected hydraulic pumps.
- the swivel position of the swivel lever is due to the prevailing in the working lines of the hydraulic pumps Working pressures and on the other hand through the regulating the delivery volume of the hydraulic pumps Control pressure specified.
- the working pressures engage on a suitable actuator Attack element that pivots the pivot lever of the hyperbola controller.
- the Lever arm via which the engagement element acts on the pivot lever, is by another actuator set by the control pressure of the control pressure line is applied.
- the control pressure is a measure of the delivery volume of the hydraulic pumps is ultimately the product from the power control device according to the invention the working pressures of the hydraulic pumps and the delivery volume of the hydraulic pumps limits a predetermined maximum value.
- the working pressures of the hydraulic pumps can either, as in EP 0 133 870 A1, via a diaphragm seal on the actuator act or any working line can be guided to the actuator, so that Actuator from the possibly weighted sum of the working pressures of the individual Work lines is applied.
- the power control device according to the invention can be independent of the hydraulic pumps are arranged and is only hydraulic via the control pressure line with the Adjustment devices of the hydraulic pumps connected. A mechanical connection between the pivot lever of the power control device and the adjustment devices the hydraulic pumps are not required.
- the power control device according to the invention is therefore for Suitable for controlling hydraulic pumps of different types.
- the Hydraulic pumps can also be arranged at a distance from one another, even then only a single hyperbolic regulator with a single rocker arm is required. For the The power control device according to the invention therefore has a wide field of use.
- the actuating element acting on the swivel lever via the engagement element can according to claim 2 with both the first and the second working line be connected.
- the control element via the control element to connect a diaphragm seal to the working lines.
- the attack element the swivel lever displacing the lever arm fixing actuator is with the Control pressure line connected and can work according to claim 3 so that the Lever arm inversely proportional to the control pressure prevailing in the control pressure line is.
- the control pressure can by the control pressure valve according to claim 4 from the Working pressure can be derived.
- the control pressure valve can be operated via a shuttle valve each connected to the work line that has the highest working pressure leads.
- the supply for the control pressure can also come from a other pressure source.
- the control pressure valve can be designed as a 3/2-way valve and be connected to the pivot lever so that with increasing exposure to the Swivel lever through the engagement element of the control pressure on the control line is increasingly increasing.
- the control pressure valve according to Claim 6 additionally by means of an electromagnet by an electrical control signal be applied to vary the limiting power depending on the to enable electrical control signal.
- a further hydraulic pump can be provided, the working line additionally connected to the actuating element acting on the engagement element is.
- this further hydraulic pump can also be adjustable and the control pressure regulated by the control pressure valve can be the adjusting device this additional hydraulic pump can also be supplied, so that this additional Hydraulic pump from the power control device according to the invention in synchronism with the other hydraulic pumps is controlled.
- control line can be in control pressure branch lines branch, each to the adjustment devices of the individual lockable hydraulic pumps lead and each have a check valve for decoupling.
- Pressure relief valves can be provided according to claim 10. These pressure relief valves respond when the working pressure in the assigned Working line exceeds a predetermined threshold. Due to the pressure increase in the corresponding control pressure branch line is pivoted back the assigned Hydropump causes and pressure overload of the work line avoided.
- a third actuator can be provided that does not have the attack element which is displaceable with respect to its lever arm, but directly on acts on the swivel lever.
- the third control element it is possible to control the priority in such a way that one connected to the third actuator Working line of another hydraulic pump the performance of that of the invention Capacity control device controlled hydraulic pumps, if this further Hydraulic pump is activated.
- the power control device in the exemplary embodiment shown in FIG. 1, is generally provided with the reference number 1.
- the power control device 1 is used to control two adjustable hydraulic pumps 2 and 3. Zur Each hydraulic pump 2, 3 has an adjustment device 4 for adjusting the delivery volume or 5 on.
- the hydraulic pumps 2, 3 each feed into separate working lines 6 and 7.
- the working lines 6 and 7 are via a shuttle valve 8 and a connecting line 9 connected to a control pressure valve 10.
- the control pressure valve 10 is shown in Embodiment designed as a 3/2-way valve and via a control line 11 with the Adjustment devices 4 and 5 of the two hydraulic pumps 2 and 3 connected.
- In the in Fig. 1 basic position shown is the connecting line 9 via the control pressure valve 10 with a pressure fluid tank 12 in connection.
- a pivot lever 13 of a hyperbola controller 16 is L-shaped in the exemplary embodiment and rotatable about an axis 14 stored. The pivot lever 13 acts on the control pressure valve 10 via a tappet 15 on.
- the control pressure line 11 With increasing pivoting of the pivot lever 13 in the embodiment in The control pressure line 11 becomes increasingly clockwise with the connecting line 9 connected and thus increasingly subjected to control pressure.
- To pivot the Swivel lever 13 serves an engagement element 17 which is parallel to the arm 18 of the Swivel lever 13 is displaceable, as indicated by arrow 19.
- the engagement element 17 can move by means of a wheel 20 on the arm 18 of the pivot lever 13 in a rolling manner.
- a first one is used to move the engagement element 17 along the arrow direction 19 Control element 21, which is connected to the control pressure line 11 and with which in the Control pressure line 11 prevailing control pressure is applied.
- the first actuator 21 shifts the engagement element 17 against a preferably adjustable return spring 22.
- the first actuating element 21 defines the lever arm with which the Attack element 17 on the pivot lever 13 pivotable about the pivot axis 14 attacks.
- a second Actuator 24 which via connecting lines 25 and 26 to the working lines 6 and 7 is connected.
- the exemplary embodiment shown in FIG. 2 acts via the ratio of Measuring areas weighted sum of the prevailing in the working lines 6 and 7 Working pressures on the attack element 17.
- An electromagnet 27 can be provided on the pressure control valve 10 in order to prevent the power control device 1 limited maximum power output of the Influence hydraulic pumps 2 and 3 as a function of an electrical control signal to be able to.
- the function of the power control device 1 according to the invention is as follows:
- the adjusting devices pivot 4 and 5 e.g. due to suitable springs, the hydraulic pumps 2 and 3 maximum funding volume.
- the hydraulic pumps 2 and 3 then pump into them assigned working lines 6 and 7 and on the second actuating element 24 Pressure that presses the attack element 17 in Fig. 1 upwards and corresponding to the Swivel lever 13 pivoted clockwise against the return spring 23.
- Thereby increasingly opens the control pressure valve 10 and the control pressure line 11 is via the Connection line 9 and the shuttle valve 8 with pressure from the working lines 6 and 7 acted upon.
- FIG. 1 branches the control line 11 at a branch point 28 in two control pressure branch lines 29 and 30, which each lead to one of the adjustment devices 4 and 5.
- a check valve 31 or 32 is provided for Decoupling of the two control pressure branch lines 29 and 30 is in each control pressure branch line 29 or 30, a check valve 31 or 32 is provided.
- the control pressure branch lines 29 and 30 are via throttles 33 and 34 with the pressure fluid tank 12 connected.
- a pressure relief valve 35 or 36 arranged between the working lines 6 and 7 or between the connecting lines 25 and 26 and the control pressure branch lines 30 and 29 is corresponding to that Further development according to the invention in each case a pressure relief valve 35 or 36 arranged.
- Valve spring 37 or 38 adjustable maximum pressure If the working pressure in the working line 6 or 7 exceeds one by Valve spring 37 or 38 adjustable maximum pressure, the corresponding one opens Pressure relief valve 35 or 37 and thus increases the pressure in the associated Control pressure branch line 29 or 30. As a result, the corresponding hydraulic pump 2 or 3 pivoted back until the working pressure in the corresponding working line 6 or 7 falls below the specified maximum pressure again.
- the pressure advantageously the for the power control already existing control pressure line 11 for the Pressure limitation is also used.
- FIG. 2 shows a second exemplary embodiment of the power control device according to the invention.
- the elements already described have the same reference numerals provided, so that a repetitive description is unnecessary.
- the difference between the exemplary embodiment shown in FIG. 2 and that based on 1 already described embodiment essentially consists in that by the power control device 1 according to the invention in addition to the first and second Hydraulic pump 2 and 3 is also controlled a third hydraulic pump 40, which is in a third Work management 41 promotes.
- the third working line 41 is via a further connecting line 42 connected to the second actuating element 24, so that the engagement element 17 with the possibly weighted sum of the prevailing in the work lines 6, 7 and 41 Working pressures is applied.
- the control line 11 branches to the Branch point 28 into a third control pressure branch line 43, which is from the Branch point 28 is separated by a third check valve 44.
- the third Control pressure branch line 43 leads to the adjusting device 45 of the third hydraulic pump 40.
- the third control pressure branch line 43 is connected via a throttle 46 to the Pressurized fluid tank 12 connected.
- A serves to secure the third working line 42 third pressure relief valve 47, which between the connecting line 42 and the Control pressure branch line 43 is arranged.
- more than three adjustable hydraulic pumps can also be operated by the power control device 1 according to the invention can be controlled.
- Power control device 1 is in addition to the two hydraulic pumps 2 and 3 further hydraulic pump 50 is provided, which feeds into a third working line 51.
- the Elements already described with reference to FIG. 1 are also identical here Provide reference numerals to facilitate the assignment.
- the second actuating element 24 consists of a first actuating chamber 52 and a second actuating chamber 53, so that both on the engagement element 17 the working pressure of the first working line 6 and the working pressure of the second Working line 7 can attack.
- hydraulic pump 50 is not connected to control line 11. There is also none Connection between the second actuator 24 and the third working line 51. Die rather, the third working line 51 is connected via a connecting line 54 to a third, directly connected to the pivot lever 13 engaging actuator 55.
- the third actuating element 55 has a pressure chamber 56 which is connected to the connecting line 54 is connected and acts on a piston 57 against a return spring 58. Of the Piston 57 presses via a plunger 59 on the pivot lever 13. If in the third Working line 51 no or only a low working pressure is present Return spring 58 unhindered via the plunger 59 on the pivot lever 13 and Spring forces of the return spring 23 and the return spring 58 add up. However, as soon as A sufficient working pressure is present on the working line 51, the piston 57 in Fig. 3 moved to the right so that the plunger 59 lifts off the pivot lever 13.
- the third hydraulic pump 50 therefore comes a certain Priority because when starting the third hydraulic pump 50 and a corresponding Working pressure in the third working line 51 is the power that the first hydraulic pump 2 and can deliver the third hydraulic pump 3 is reduced. On the third hydraulic pump 50 can therefore be connected to a consumer with high performance priority.
- FIG. 4 shows a fourth exemplary embodiment of the power control device according to the invention 1, where elements already described with matching reference numerals are provided.
- a third hydraulic pump 40 Similar to the embodiment shown in Fig. 2 is a third hydraulic pump 40 provided, the working line 41 via a connecting line 42 to the second Actuator 24 is connected. For this purpose, there is one in the second actuating device 24 additional pressure chamber 60 is provided. The possibly acting on the attack element 17 weighted sum of the working pressures in the three working lines 6, 7 and 41.
- the third hydraulic pump 40 in the embodiment shown in FIG. 4 not as Variable pump, but designed as a constant pump and therefore not with the Control line 11 connected.
- a fourth hydraulic pump 50 is provided, the working line 51 via a Connecting line 54 is connected to the described third actuator 55 the performance characteristics of the power device 1 for the first hydraulic pump 2 and the to influence the second hydraulic pump 3 as already described with reference to FIG. 3. To that The work line 51 connected consumer therefore comes with this configuration a certain priority too.
- FIG. 5 shows a fifth exemplary embodiment of the power control device according to the invention 1. Again, there are already different elements with matching ones Provide reference numerals.
- the difference from the exemplary embodiment shown in FIG. 4 and already described consists essentially in that the third hydraulic pump 40 is not as Constant pump is designed as a variable displacement pump. Your adjustment device 45 is thereby in a manner similar to that in the embodiment shown in FIG. 2 via a Control pressure branch line 42 connected to the control pressure line 11 and is through the Power control device 1 according to the invention also regulated.
- the Power control device 1 on hydraulic pumps with different nominal pressures or Sizes are adjusted, with the individual working pressures then being assigned Measuring areas are weighted. Due to the hyperbolic performance characteristic is a good one Performance utilization of the individual hydraulic pumps possible.
- the invention Power control device 1 can be used for a wide variety of pump types, pump combinations and pump sizes are used. The multiple use of the invention Power control device 1 for different pump types and pump combinations increases the number of pieces and decreases the number of controller variants, resulting in a Cost reduction helps. Interventions or a change in the performance characteristics are possible without much effort.
- the adjustment work on the individual hydraulic pumps 2, 3, 40, 50 is significantly simplified.
- the power control device 1 according to the invention can independent of the adjustment devices 4, 5, 45 of the hydraulic pumps 2, 3 and 40 can be set. A subsequent change in performance is through simple exchange the power control device 1 easily possible.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Operation Control Of Excavators (AREA)
Abstract
Description
- Fig. 1
- ein erstes Ausführungsbeispiel der erfindungsgemäßen Leistungsregeleinrichtung,
- Fig. 2
- ein zweites Ausführungsbeispiel der erfindungsgemäßen Leistungsregeleinrichtung,
- Fig. 3
- ein drittes Ausführungsbeispiel der erfindungsgemäßen Leistungsregeleinrichtung,
- Fig. 4
- ein viertes Ausführungsbeispiel der erfindungsgemäßen Leistungsregeleinrichtung, und
- Fig. 5
- ein fünftes Ausführungsbeispiel der erfindungsgemäßen Leistungsregeleinrichtung.
Claims (11)
- Leistungsregeleinrichtung (1) zum Begrenzen der Leistung zumindest einer ersten und einer zweiten an der Leistungsregeleinrichtung (1) angeschlossenen, mittels zumindest einer Verstellvorrichtung (4, 5) verstellbaren und in jeweils eine Arbeitsleitung (6, 7) fördernden Hydropumpe (2, 3)
mit einem Hyperbelregler (16), der über einen Schwenkhebel (13) auf ein Steuerdruckventil (10) zurückwirkt und einem Angriffselement (17), das auf dem Schwenkhebel (13) so verschiebbar ist, daß der Hebelarm, mit welchem das Angriffselement (17) an dem Schwenkhebel (13) angreift, veränderbar ist, wobei das Angriffselement (17) mit den in den Arbeitsleitungen (6, 7) herrschenden Arbeitsdrücken beaufschlagt ist,
dadurch gekennzeichnet,
daß für die erste und zweite Hydropumpe (2, 3) jeweils eine separate Verstellvorrichtung (4, 5) vorgesehen ist und die Leistungsregeleinrichtung (1) als von den Verstellvorrichtungen (4, 5) baulich getrennte Ventileinheit ausgebildet ist, und daß durch das Steuerdruckventil (10) ein Steuerdruck geregelt wird, der der Verstellvorrichtung (4, 5) sowohl der ersten als auch der zweiten Hydropumpe (2, 3) zum Verstellen des Fördervolumens über eine Steuerdruckleitung (11) zugeführt wird, und der Hebelarm, mit welchem das Angriffselement (17) an dem Schwenkhebel (13) angreift, durch ein erstes Stellelement (21) festgelegt ist, das mit der Steuerdruckleitung (11) verbunden ist. - Leistungsregeleinrichtung nach Anspruch 1,
dadurch gekennzeichnet,
daß die erste Hydropumpe (2) in eine erste Arbeitsleitung (6) und die zweite Hydropumpe (3) in eine zweite Arbeitsleitung (7) fördert und daß ein zweites Stellelement (24) sowohl mit der ersten als auch mit der zweiten Arbeitsleitung (6, 7) verbunden ist und das Angriffselement (17) und den Schwenkhebel (13) gegen eine erste Rückstellfeder (23) beaufschlagt. - Leistungsregeleinrichtung nach Anspruch 1 oder 2,
dadurch gekennzeichnet,
daß das erste Stellelement (21) das Angriffselement (17) gegen eine zweite Rückstellfeder (22) verschiebt, wobei das Angriffselement (17) an dem Schwenkhebel (13) mit einem Hebelarm angreift, der umgekehrt proportional zu dem Steuerdruck ist. - Leistungsregeleinrichtung nach einem der Ansprüche 1 bis 3,
dadurch gekennzeichnet,
daß das Steuerdruckventil (10) über ein Wechselventil (8) so mit den Arbeitsleitungen (6, 7) der ersten und zweiten Hydropumpen (2, 3) verbunden ist, daß dem Steuerdruckventil (10) jeweils der höchste Arbeitsdruck der ersten und zweiten Hydropumpe (2, 3) zugeführt wird. - Leistungsregeleinrichtung nach Anspruch 4,
dadurch gekennzeichnet,
daß das Steuerdruckventil (10) ein 3/2-Wegeventil ist, dessen erster Anschluß mit dem Wechselventil (8), dessen zweiter Anschluß mit einem Druckfluid-Tank (12) und dessen dritter Anschluß mit der Steuerleitung (11) verbunden ist, wobei das Steuerdruckventil (10) so mit dem Schwenkhebel (13) verbunden ist, daß mit zunehmender Beaufschlagung des Schwenkhebels (13) durch das Angriffselement (17) der Steuerdruck in der Steuerleitung (11) zunehmend erhöht wird. - Leistungsregeleinrichtung nach einem der Ansprüche 1 bis 5,
dadurch gekennzeichnet,
daß das Steuerdruckventil (10) mit einem Elektromagneten (27) zusätzlich beaufschlagbar ist. - Leistungsregeleinrichtung nach einem der Ansprüche 1 bis 6,
dadurch gekennzeichnet,
daß zumindest eine weitere Hydropumpe (40) vorgesehen ist, deren Arbeitsleitung (41) mit dem zweiten Stellelement (24) zusätzlich verbunden ist. - Leistungsregeleinrichtung nach Anspruch 7,
dadurch gekennzeichnet,
daß die weitere Hydropumpe (40) verstellbar ist und der von dem Steuerdruckventil (10) geregelte Steuerdruck über die Steuerdruckleitung (11) einer Verstellvorrichtung (45) der weiteren Hydropumpe (40) zugeführt wird. - Leistungsregeleinrichtung nach einem der Ansprüche 1 bis 8,
dadurch gekennzeichnet,
daß sich die Steuerleitung (11) in Steuerdruck-Zweigleitungen (29, 30, 43) verzweigt, die zu den Verstellvorrichtungen (4, 5, 45) der verstellbaren Hydropumpen (2, 3, 40) führen und die jeweils ein Rückschlagventil (31, 32, 44) aufweisen. - Leistungsregeleinrichtung nach Anspruch 9,
dadurch gekennzeichnet,
daß jede Arbeitsleitung (6, 7, 41) über jeweils ein Druckbegrenzungsventil (35, 36, 47) mit der zu der Verstellvorrichtung (4, 5, 45) der zugeordneten Hydropumpe (2, 3, 40) führenden Steuerdruck-Zweigleitung (29, 30, 43) stromabwärts der Rückschlagventile (31, 32, 44) verbunden ist. - Leistungsregeleinrichtung nach einem der Ansprüche 1 bis 10,
dadurch gekennzeichnet,
daß zumindest eine weitere Hydropumpe (50) vorgesehen ist, deren Arbeitsleitung (51) mit einem unmittelbar auf den Schwenkhebel (13) einwirkenden dritten Stellelement (55) verbunden ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19808127 | 1998-02-26 | ||
DE19808127A DE19808127C2 (de) | 1998-02-26 | 1998-02-26 | Leistungsregeleinrichtung |
Publications (3)
Publication Number | Publication Date |
---|---|
EP0939225A2 true EP0939225A2 (de) | 1999-09-01 |
EP0939225A3 EP0939225A3 (de) | 2000-06-14 |
EP0939225B1 EP0939225B1 (de) | 2005-04-27 |
Family
ID=7858994
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP99103324A Expired - Lifetime EP0939225B1 (de) | 1998-02-26 | 1999-02-19 | Leistungsregeleinrichtung für mehrere verstellbare Hydropumpen |
Country Status (2)
Country | Link |
---|---|
EP (1) | EP0939225B1 (de) |
DE (2) | DE19808127C2 (de) |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1304482A2 (de) * | 2001-10-18 | 2003-04-23 | Brueninghaus Hydromatik Gmbh | Summenleistungsregler und Druckmittler |
EP3045723A1 (de) * | 2015-01-16 | 2016-07-20 | HAWE Hydraulik SE | Axialkolbenpumpe |
CN111779649A (zh) * | 2020-06-30 | 2020-10-16 | 潍柴动力股份有限公司 | 一种变功率控制装置及液压*** |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0133870A1 (de) | 1983-06-28 | 1985-03-13 | Hydromatik GmbH | Regelvorrichtung für mehrere aus hydrostatischen Getrieben bestehende Antriebsaggregate |
DE4208925C1 (de) | 1992-03-19 | 1993-06-03 | Hydromatik Gmbh, 7915 Elchingen, De |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1453518A1 (de) * | 1964-09-30 | 1969-03-27 | Linde Ag | Steuerorgan fuer die Steuerung von mehreren hydrostatischen Einheiten |
DE1922145A1 (de) * | 1969-04-25 | 1970-10-29 | Bellows Valvair Kaemper Gmbh | Kombinationsregler |
DE3217360A1 (de) * | 1982-05-08 | 1983-11-10 | Robert Bosch Gmbh, 7000 Stuttgart | Regeleinrichtung fuer eine verstellbare pumpe |
JP2505457B2 (ja) * | 1987-05-01 | 1996-06-12 | カヤバ工業株式会社 | ピストンポンプの馬力制御装置 |
JP2579194B2 (ja) * | 1988-08-01 | 1997-02-05 | 株式会社小松製作所 | 可変吐出量ポンプの制御装置 |
DE19626793C1 (de) * | 1996-07-03 | 1997-06-26 | Brueninghaus Hydromatik Gmbh | Hydraulische Regeleinrichtung zum parallelen Regeln mehrerer hydrostatischer Verstellpumpen |
DE19756600C1 (de) * | 1997-12-18 | 1999-08-26 | Brueninghaus Hydromatik Gmbh | Leistungsregelventil |
-
1998
- 1998-02-26 DE DE19808127A patent/DE19808127C2/de not_active Expired - Fee Related
-
1999
- 1999-02-19 EP EP99103324A patent/EP0939225B1/de not_active Expired - Lifetime
- 1999-02-19 DE DE59911964T patent/DE59911964D1/de not_active Expired - Fee Related
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0133870A1 (de) | 1983-06-28 | 1985-03-13 | Hydromatik GmbH | Regelvorrichtung für mehrere aus hydrostatischen Getrieben bestehende Antriebsaggregate |
DE4208925C1 (de) | 1992-03-19 | 1993-06-03 | Hydromatik Gmbh, 7915 Elchingen, De |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP1304482A2 (de) * | 2001-10-18 | 2003-04-23 | Brueninghaus Hydromatik Gmbh | Summenleistungsregler und Druckmittler |
EP1304482A3 (de) * | 2001-10-18 | 2005-09-07 | Brueninghaus Hydromatik Gmbh | Summenleistungsregler und Druckmittler |
EP3045723A1 (de) * | 2015-01-16 | 2016-07-20 | HAWE Hydraulik SE | Axialkolbenpumpe |
CN111779649A (zh) * | 2020-06-30 | 2020-10-16 | 潍柴动力股份有限公司 | 一种变功率控制装置及液压*** |
Also Published As
Publication number | Publication date |
---|---|
DE19808127A1 (de) | 1999-09-09 |
EP0939225A3 (de) | 2000-06-14 |
EP0939225B1 (de) | 2005-04-27 |
DE19808127C2 (de) | 1999-12-09 |
DE59911964D1 (de) | 2005-06-02 |
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