EP1304482A2 - Summenleistungsregler und Druckmittler - Google Patents
Summenleistungsregler und Druckmittler Download PDFInfo
- Publication number
- EP1304482A2 EP1304482A2 EP02016036A EP02016036A EP1304482A2 EP 1304482 A2 EP1304482 A2 EP 1304482A2 EP 02016036 A EP02016036 A EP 02016036A EP 02016036 A EP02016036 A EP 02016036A EP 1304482 A2 EP1304482 A2 EP 1304482A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- pressure
- measuring
- control
- diaphragm seal
- 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
- F04B2205/06—Pressure in a (hydraulic) circuit
-
- 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
- F04B2205/06—Pressure in a (hydraulic) circuit
- F04B2205/061—Pressure in a (hydraulic) circuit after a throttle
-
- 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
- F04B2205/06—Pressure in a (hydraulic) circuit
- F04B2205/062—Pressure in a (hydraulic) circuit before a throttle
-
- 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
- F04B2205/18—Pressure in a control cylinder/piston unit
Definitions
- the invention relates to a total power controller for Regulation of the total power of several hydrostatic Piston machines and a diaphragm seal for generation a medium pressure for power control.
- Capacity regulator for regulating funding of several hydrostatic piston machines, which by a common drive source are known.
- DE 33 23 278 C2 is a device disclosed, in which a total of three hydraulic pumps from one common drive machine are driven. The pumps convey a pressure medium into one assigned Working line. At least two of the hydraulic pumps are executed adjustable, the adjustment devices of the two hydraulic pumps together via a so-called Hyperbolic controls are adjustable. To operate the Adjustment device of the two hydraulic pumps is on Actuating piston, the two opposite piston surfaces has on one side with one of the two Working lines of the hydraulic pumps to be adjusted averaged pressure depressed. This first piston surface is with the second piston surface opposite it a channel and a control valve arranged therein connected.
- the position of the Control valve is the pressure on the second piston surface between the average working pressure as the maximum and the Tank pressure regulated as minimum pressure.
- the position of the Control valve is the average of the pressure Working lines and the position of the control piston dependent.
- the position of the control piston the swivel angle and thus the delivery volume of the adjustable hydraulic pumps are taken into account.
- the one from the third hydraulic pump consumed power is thereby takes into account that that generated by the third pump Pressure in the work line via a lever mechanism on the Control valve is transmitted and thus its position affected.
- a diaphragm seal used to generate the averaged Working line pressure is used, for example known from DE 34 07 827 C2.
- the diaphragm seal includes one Step piston, which is axially in a valve housing is slidably arranged. He points two in the same direction oriented stepped piston surfaces, each with the Working lines of the piston machines to be adjusted are connected. The radially outer limits of the Stepped piston surfaces form with the valve housing in each case a variable throttle.
- the two chokes are in Dependent on the position of the stepped piston together variable.
- the output side of the chokes is over one common supply line with one against the Step piston surfaces oriented sum piston surface connected.
- Each choke has its own assigned check valve arranged on the outlet side, which opens in the direction of the total piston area. The Cumulative piston area is thus only by the greater pressure of the working lines with pressure medium provided.
- the described device for regulating the total power of several hydrostatic piston machines Disadvantage that to take into account a third hydrostatic piston machine a complicated tuning of leverage is required to increase their performance consider. Another disadvantage is that the two Variable pumps are only adjustable together. The proposed arrangement is therefore only suitable for the Operation of two identical hydraulic pumps in connection with a third hydraulic pump, which is used to control the Funding is not taken into account.
- the diaphragm seal used also has the disadvantage that the Stepped piston surfaces simultaneously as variable throttles are trained. This leads to the operation of the diaphragm seal the stepped piston surfaces from the flowing medium be depressed. By directly conveying yourself changing volume during an actuating movement of the actuating piston can large volume flows in the diaphragm seal occur. The positioning accuracy of the diaphragm seal is thereby reduced.
- the invention has for its object a Total power control and a diaphragm seal easier Design for several hydrostatic piston machines too create which over which one Control parameters and the operation of hydraulic pumps various services.
- the total power controller according to the invention has the advantage that for each piston machine an individual Actuating device is provided. At the same time, as Control parameters used a common size that on the Control characteristic of the piston machines acts together. This will make each other's performance Piston engines primary from the same Drive engine are taken into account.
- the actual actuating energy is the respective Piston machine removed via the working line itself. Because of the diaphragm seal, there are therefore only small volume flows necessary. This small volume flow is influenced by the separate arrangement of the stepped piston surfaces and the Control edges not the control accuracy of the diaphragm seal.
- the variability is also due to the Hyperbolic regulator arranged measuring pistons enlarged. From one Threshold for the mean pressure, that for all Piston engines can be the same or different the influence of a second spring is switched off, resulting in a second possibly different control characteristic is available. A coordination of the total power controller is therefore also for piston machines with different maximum outputs possible.
- Fig. 1 is a hydraulic circuit diagram of a total power control device according to the invention shown, in which a drive machine 1 via an output shaft 2 and a reduction gear 3 with three hydrostatic Piston machines 5, 5 'and 5 "is connected
- a drive machine 1 via an output shaft 2 and a reduction gear 3 with three hydrostatic Piston machines 5, 5 'and 5 "is connected
- hydrostatic piston machines 5, 5 'and 5' 'equivalent components will be easier Understandability to mention the simply deleted or two crossed out reference numerals.
- the countershaft 3 driven by the drive machine 1 is by means of a drive shaft 4 with the hydrostatic Piston engine 5 connected.
- the hydrostatic Piston machine 5 is adjustable in its delivery volume executed. From the hydrostatic piston machine 5 a suitable pressure medium in a working line 6 promoted.
- the adjustment of the delivery volume of the hydrostatic Piston engine 5 is operated by a hyperbola controller 7 regulated, which is described below with reference to FIG. 2 is explained in more detail and essentially one Adjustment device 8, a reset device 9 and a control valve 10 and a volumetric piston 11 comprises.
- all three Hyperbola controllers 7, 7 'and 7 one from a diaphragm seal 12 averaged pressure supplied.
- the one from the diaphragm seal 12 average pressure is in an outlet pressure line 13 to Provided.
- the average is Output pressure on from in the working lines 6, 6 'and 6 "prevailing arithmetic working pressures Average.
- Via working pressure connection lines 14, 14 ' and 14 are the working lines 6, 6 'and 6" with the Diaphragm seals 12 connected.
- In the Connection line 15 is the highest available pressure of the working lines 6, 6 'and 6 ".
- the pressure prevailing in the outlet pressure line 13 becomes set by a 3/2-way valve 19 so that the sum the forces acting on measuring surfaces 17, 17 'and 17' ' the same size as the one facing the opposite Total area 18 is acting force.
- the total area 18 is for this purpose via a feedback line 22 with the Output pressure line 13 connected.
- the measuring surfaces 17, 17 ' and 17 are correspondingly via measuring pressure lines 23, 23 ' and 23 "with the corresponding Working pressure connection lines 14, 14 'and 14' ' connected.
- the 3/2 way valve 19 is between two end positions freely adjustable, whereby the position of the 3/2-way valve depending on the resulting force the measuring surfaces 17, 17 'and 17' 'and the opposing total area 18 sets.
- the 3/2-way valve connects the first end position Connection line 15 with the outlet pressure line 13.
- In the second end position becomes the outlet pressure line 13 via a return line 20 with a tank volume 21 connected, so that in the outlet pressure line 13th prevailing pressure against the tank volume 21 relaxed becomes.
- the 3/2 way valve 19 can be any Take intermediate position.
- the hydrostatic piston machine 5 is regulated by means of the adjusting device 8, which adjusts the hydrostatic piston machine 5 in the direction of a large swivel angle and thus a large delivery volume V max .
- the hydrostatic piston machine 5 can be adjusted in the direction of the small delivery volume V min by the resetting device 9.
- the adjusting device 8 has an actuating piston 25 an actuating piston surface 25a, which in a Signal pressure chamber 26 via a signal pressure line 27 from the Working line 6 can be depressed.
- the control piston 25 against the Force of a return spring 28 axially shifted. Doing so the hydrostatic piston machine 5 in the direction of larger Swivel angle controlled.
- the actuating piston 25 is in the Adjusting piston 25 with respect to its longitudinal axis slidably mounted feedback plunger 29, whereby via a signal pressure channel from signal pressure space 26 an end face 31 of the feedback plunger 29 is pressed becomes.
- the force generated by the lever 32 on the Control valve 10 is opposed to a counterforce, which results from the force of a first compression spring 34 and a force of a second compression spring 35 is composed.
- the second compression spring 35 acts on the measuring piston 11, 36 axial forces by means of a measuring piston rod only in the direction of thrust to the control valve 10 are transferable.
- the first compression spring 34 which is directly on the Control valve acts, and the second compression spring 35 in their Preload adjustable.
- the measuring piston 11 is guided into a measuring cylinder 33 which via the supply line 24 to the outlet pressure line 13 connected is.
- the pressure prevailing in the measuring cylinder 33, the the mean pressure of the three working lines 6, 6 ' and 6 '' corresponds to a measuring piston surface 36 and reduces the one acting on the control valve 10 Axial force of the second compression spring 35.
- the control valve 10 operates depending on the force of the lever 32 and the opposite, resulting force between two end positions.
- a the first end position connects the control valve 10 Signal pressure line 27 with a reset connection line 38, which opens into the reset pressure chamber 39.
- a reset connection line 38 With the in the pressure prevailing in the reset pressure chamber 39 Surface 40a of a reset piston 40 is pressed.
- the second end position is one of the control valve 10 Connection between the reset connection line 38 and the tank volume 21 produced.
- the control valve 10 controls the ratio of those in the Actuating pressure chamber 26 and the return pressure chamber 29 acting Pressures depending on the power of the piston machine 5.
- the lever 32 is on the control valve 10 one opposite to the two compression springs 34 and 35 Control force generated, which is proportional to the power.
- Control force generated which is proportional to the power.
- increases in the work line 6 pressure generated by the hydrostatic piston machine 5 so is on the signal pressure line 27 and Signal pressure channel 30 on the end face 31 of the Feedback plunger 29 also increased force effective, which acts in point of attack A and thus that Control valve 10 towards its first end position adjusted.
- By adjusting the control valve 10 in Towards its first end position Signal pressure line 27 increasingly with Reset connection line 38 connected.
- the influence of the second compression spring 35 is infinitely variable reduce. If the average pressure exceeds one certain threshold value, the measuring piston rod 36 lifts completely from the control valve 10 and by the Deflection lever 32. Control force generated on the control valve 10 is only directed against the first compression spring 34. By reducing the spring force which the Counteracts regulating force, the pressure ratio in the Signal pressure chamber 26 and the reset pressure chamber 39 see above changed that the hydrostatic piston machine 5 in Is adjusted in the direction of a smaller swivel angle.
- FIG. 3 A constructive implementation of the embodiment of inventive total power controller and Diaphragm seal is shown schematically in Fig. 3.
- the control valve 10 has a control piston 41, which in Dependence on the resulting force acting on it from the regulating force acting on the one hand and the sum the opposing force of the first Compression spring 34 and through it on the measuring piston surface 37 acting reduced force of the second compression spring 35 is axially displaceable.
- a first control edge 42 and a second control edge 43 educated.
- By opening the through the first control edge 42 formed throttle the signal pressure line 27 increasingly with the Reset connection line 38 connected. Accordingly the connection between the reset connection line 38 and the tank 21 by reducing the cross section the second throttle of the control edge 43 closed. Is the hydrostatic piston machine 5 by pressing the Reset pressure chamber 39 to its minimum pivot angle is set, the reset pressure chamber 39 via an in the relief line 44 arranged in the reset piston 40 connected to the tank 21.
- the diaphragm seal 12 a two-part stepped piston 45, 46, one first step piston part 45 and a second Step piston part 46 includes.
- the two stepped piston parts 45 and 46 are slidable in a valve body 70 angeordent.
- On the first step piston part 45 there is one first measuring surface 17, a second measuring surface 17 'and a third measuring surface 17 '' arranged.
- the three input pressures to be generated are the three Measuring surfaces 17, 17 'and 17' 'of the same size.
- the three Measuring surfaces 17, 17 'and 17' ' are the end faces of the Cross-sectional changes of the first step piston part 45 trained and oriented in the same direction.
- the three formed in front of the measuring surfaces 17, 17 'and 17' ' Volumes between the first step piston part 45 and the Valve body 70 are each via a measuring pressure line 23, 23 'and 23' 'and the corresponding ones Working pressure lines 14, 14 'and 14' 'with the corresponding pressure of the working lines 6, 6 'and 6 " depressed.
- the working pressure lines 14 and 14 ' are with two inputs of a first shuttle valve 47 connected.
- the output line 49 of the shuttle valve 47 is with a Input of a second shuttle valve 48 connected second input connected to the working pressure line 14 '' is.
- the output of the second shuttle valve 48 is with the Connection line 15 connected.
- first and second control edge 50 and 51 form two together with the valve body 70 variable throttling points.
- a connection between the connecting line 15 and the Output pressure line 13 can be produced.
- the second Control edge 51 and the variable throttle formed therewith the outlet pressure line 13 can be connected to the tank 21.
- That of the sum piston surface 18 and the valve body 70 enclosed volume 71 is about the Feedback line 22 with the outlet pressure line 13 connected.
- Due to the measuring surfaces 17, 17 'and 17' ' and the oppositely oriented total area 18 generated forces are the first step piston part 45 and the second stepped piston part 46 on a contact surface 52 in Plant held. The position of thus common displaceable piston parts 45 and 46 is so adjusted that the two stage piston parts 45 and 46 are in the equilibrium of forces.
- One around Contact surface 52 formed space 72 in the valve body 70 is connected to the tank via a further relief line 60 21 connected.
- hydrostatic piston machines 5, 5 'and 5' ' With the described diaphragm seal 12 and thus connected total power control, it is easily possible also hydrostatic piston machines 5, 5 'and 5' 'with one to operate common control parameters if the hydrostatic piston machines 5, 5 'and 5' ' have different power ratings.
- the setting the power shares of the hydrostatic piston machines 5, 5 'and 5' ' is preferably such that the force which by the first compression spring 34 and the second Compression spring 35 on the control piston 41 of the control valve 10 is generated, 100% of the performance of the assigned hydrostatic piston machine 5, 5 'or 5 "corresponds. Is the pressure averaged by the diaphragm seal 12 in the Outlet pressure line 13 so large that the volumetric piston 11 from the control piston 41, so the hydrostatic Piston engine 5 a power control, which is determined exclusively by the first compression spring 34.
- the use of a split step piston 45, 46 with a first step piston part 45 and a second Stepped piston part 46 facilitates the manufacture of the Diaphragm seal 12 according to the invention considerably. tension as they did by editing a one-piece Stepped piston could arise during operation, are thus avoided and the regulation works accordingly more precise.
- the invention Total power controller is also for use in systems suitable with more than three hydrostatic piston machines.
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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)
Abstract
Description
- Fig. 1
- einen hydraulischen Schaltplan für eine Summenleistungsregelung an drei hydrostatischen Kolbenmaschinen;
- Fig. 2
- eine vergrößerte Darstellung im Ausschnitt II der Fig. 1; und
- Fig. 3
- eine schematische Darstellung eines Ausführungsbeispiels des erfindungsgemäßen Summenleistungsreglers.
Claims (12)
- Summenleistungsregler für mehrere hydrostatische Kolbenmaschinen (5, 5', 5''), deren Fördervolumen mittels Verstellvorrichtungen (8, 9, 8', 9', 8'', 9'') einstellbar ist und die ein Druckmittel in Arbeitsleitungen (6, 6', 6'') fördern, wobei die Verstellvorrichtungen (8, 9, 8', 9', 8'', 9'') durch eine Hyperbelregelvorrichtung (7, 7', 7'') regelbar sind und der Arbeitsdruck der hydrostatischen Kolbenmaschinen (5, 5', 5'') einem Druckmittler (12) zugeführt wird,
dadurch gekennzeichnet, daß für jede Verstellvorrichtung(8, 9, 8', 9', 8'', 9'') der hydrostatischen Kolbenmaschinen (5, 5', 5'') eine separate Hyperbelregelvorrichtung (7, 7', 7'') vorgesehen ist, der einen Regelkolben (41, 41', 41'') und einen Meßkolben (11, 11', 11'') umfaßt, wobei der Meßkolben (11, 11', 11'') durch eine Axialkraft vorbelastet ist, welche auf den Regelkolben (41, 41', 41") übertragbar ist, und der eine Kraft entgegengerichtet ist, die durch einen von dem Druckmittler (12) gemittelten Druck an einer Meßkolbenfläche (37, 37', 37'') erzeugt wird. - Summenleistungsregler nach Anspruch 1,
dadurch gekennzeichnet, daß zur Erzeugung der Axialkraft auf den Meßkolben (11, 11', 11'') eine Druckfeder (35, 35', 35'') vorgesehen ist. - Summenleistungsregler nach Anspruch 1 oder 2,
dadurch gekennzeichnet, daß die Meßkolbenflächen (37, 37', 37'') der Meßkolben (11, 11', 11'') identisch sind. - Summenleistungsregler nach Anspruch 1 oder 2,
dadurch gekennzeichnet, daß die Meßkolbenflächen (37, 37', 37'') der Meßkolben (11, 11', 11'') unterschiedlich sind. - Summenleistungsregler nach einem der Ansprüche 1 bis 4,
dadurch gekennzeichnet, daß die Summe aller in Richtung der Axialkraft an dem Regelkolben (41, 41', 41'') angreifenden Kräfte bei druckloser Meßkolbenfläche (37, 37', 37'') gleich groß ist der in entgegengesetzter Richtung bei Nennleistung der hydrostatischen Kolbenmaschine (5, 5', 5'') an dem Regelkolben (41, 41', 41'') angreifenden Kraft. - Summenleistungsregler nach einem der Ansprüche 1 bis 5,
dadurch gekennzeichnet, daß die Hyperbelregelvorrichtung (7, 7', 7") einen Umlenkhebel (32, 32', 32'') umfaßt, auf den ein Drehmoment wirkt, das proportional zu dem Fördervolumen der hydrostatischen Kolbenmaschine (5, 5', 5'') und proportional zu dem Druck in der Arbeitsleitung (6, 6', 6'') ist, wobei der Umlenkhebel (32, 32', 32'') eine dem Drehmoment entsprechende Kraft auf den Regelkolben (41, 41', 41'') überträgt. - Summenleistungsregler nach Anspruch 6,
dadurch gekennzeichnet, daß der Umlenkhebel (32, 32', 32") in einen Drehpunkt (D, D', D") drehbar gelagert ist und auf einen ersten Schenkel (32a, 32a', 32a") des Umlenkhebels (32, 32', 32'') in einem Angriffspunkt (A, A', A") eine Kraft wirkt, die proportional zu dem in der Arbeitsleitung (6, 6', 6'') herrschenden Druck ist und daß der Abstand des Angriffspunkts (A, A', A'') von dem Drehpunkt (D, D', D'') proportional zu dem eingestellten Schwenkwinkel der hydrostatischen Kolbenmaschine (5, 5', 5'') ist und ein zweiter (32b, 32b', 32b'') Schenkel des Umlenkhebels (32, 32', 32'') die dem resultierenden Drehmoment entsprechende Kraft auf den Regelkolben (41, 41', 41'') überträgt. - Druckmittler zur Bereitstellung eines aus zumindest zwei Eingangsdrücken gemittelten Ausgangsdrucks, mit einem in einem Ventilkörper (70) in axialer Richtung verschieblich angeordneten Stufenkolben (45, 46), dessen zumindest zwei gleichsinnig angeordneten Meßflächen (17, 17', 17'') mit jeweils einem Eingangsdruck beaufschlagbar sind und einer gegensinnig zu den Meßflächen (17, 17', 17'') angeordneten Summenkolbenfläche (18), welche mit einem Ausgangsdruck beaufschlagt ist,
dadurch gekennzeichnet, daß an dem Stufenkolben (45, 46) eine erste Steuerkante (50) ausgebildet ist, welche abhängig von der axialen Position des Stufenkolbens (45, 46) in dem Ventilkörper (70) eine erste variable Drossel ausbildet, wobei eine Eingangsseite der variablen Drossel mit dem jeweils höchsten Eingangsdruck des Druckmittlers (12) beaufschlagt wird und ausgangsseitig die Summenkolbenfläche (18) des Druckmittlers (12) mit dem Ausgangsdruck beaufschlagt ist. - Druckmittler nach Anspruch 8,
dadurch gekennzeichnet, daß an dem Stufenkolben (45, 46) eine zweite Steuerkante (51) ausgebildet ist, welche eine zweite, gegensinnig zu der ersten Drossel arbeitende, mit dieser gemeinsam variable Drossel ausbildet, welche zwischen der Ausgangsdruckleitung (13) und einen Tank (21) angeordnet ist. - Druckmittler nach Anspruch 8 oder 9,
dadurch gekennzeichnet, daß der Stufenkolben einen ersten Stufenkolbenteil (45) und einen zweiten Stufenkolbenteil (46) aufweist. - Druckmittler nach Anspruch 10,
dadurch gekennzeichnet, daß die mit den Eingangsdrücken beaufschlagten Meßflächen (17, 17', 17'') in dem ersten Stufenkolbenteil (45) angeordnet sind und die Summenkolbenfläche (18) an dem zweiten Stufenkolbenteil (46) angeordnet ist. - Druckmittler nach Anspruch 10 oder 11,
dadurch gekennzeichnet, daß die erste und die zweite variable Drossel an demselben Stufenkolbenteil (46) angeordnet sind.
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP06005942A EP1683969A1 (de) | 2001-10-18 | 2002-07-18 | Summenleistungsregler und Druckmittler |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE2001151401 DE10151401A1 (de) | 2001-10-18 | 2001-10-18 | Summenleistungsregler und Druckmittler |
DE10151401 | 2001-10-18 |
Related Child Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06005942A Division EP1683969A1 (de) | 2001-10-18 | 2002-07-18 | Summenleistungsregler und Druckmittler |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1304482A2 true EP1304482A2 (de) | 2003-04-23 |
EP1304482A3 EP1304482A3 (de) | 2005-09-07 |
EP1304482B1 EP1304482B1 (de) | 2006-08-30 |
Family
ID=7702894
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06005942A Withdrawn EP1683969A1 (de) | 2001-10-18 | 2002-07-18 | Summenleistungsregler und Druckmittler |
EP20020016036 Expired - Fee Related EP1304482B1 (de) | 2001-10-18 | 2002-07-18 | Summenleistungsregler und Druckmittler |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP06005942A Withdrawn EP1683969A1 (de) | 2001-10-18 | 2002-07-18 | Summenleistungsregler und Druckmittler |
Country Status (2)
Country | Link |
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EP (2) | EP1683969A1 (de) |
DE (2) | DE10151401A1 (de) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007062887B4 (de) | 2007-12-28 | 2021-12-02 | Robert Bosch Gmbh | System zur Fixierung eines einheitlichen Exzenterbolzens |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0093916A1 (de) * | 1982-05-08 | 1983-11-16 | Robert Bosch Gmbh | Regeleinrichtung für eine verstellbare Pumpe |
DE3323278A1 (de) * | 1983-06-28 | 1985-01-17 | Hydromatik GmbH, 7915 Elchingen | Regelvorrichtung fuer mehrere aus hydrostatischen getrieben bestehende antriebsaggregate |
EP0561153A1 (de) * | 1992-03-19 | 1993-09-22 | Brueninghaus Hydromatik Gmbh | Vorrichtung zur Leistungregelung von wenigstens zwei hydrostatischen Verstellpumpen |
EP0924427A1 (de) * | 1997-12-18 | 1999-06-23 | Brueninghaus Hydromatik Gmbh | Leistungsregelventil |
EP0939225A2 (de) * | 1998-02-26 | 1999-09-01 | Brueninghaus Hydromatik Gmbh | Leistungsregeleinrichtung für mehrere verstellbare Hydropumpen |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5543245A (en) * | 1978-09-22 | 1980-03-27 | Komatsu Ltd | Volume controller of variable hydraulic pump |
DE3407827C2 (de) * | 1983-03-24 | 1985-03-28 | Hydromatik GmbH, 7915 Elchingen | Druckmittler |
DE3625222A1 (de) * | 1986-07-25 | 1988-02-04 | Index Werke Kg Hahn & Tessky | Druckregler fuer hydraulisch gesteuerte werkzeugmaschinen |
DE19735110B4 (de) * | 1997-08-13 | 2004-09-16 | Brueninghaus Hydromatik Gmbh | Regelvorrichtung mit Druckmittler |
-
2001
- 2001-10-18 DE DE2001151401 patent/DE10151401A1/de not_active Withdrawn
-
2002
- 2002-07-18 EP EP06005942A patent/EP1683969A1/de not_active Withdrawn
- 2002-07-18 DE DE50207984T patent/DE50207984D1/de not_active Expired - Fee Related
- 2002-07-18 EP EP20020016036 patent/EP1304482B1/de not_active Expired - Fee Related
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0093916A1 (de) * | 1982-05-08 | 1983-11-16 | Robert Bosch Gmbh | Regeleinrichtung für eine verstellbare Pumpe |
DE3323278A1 (de) * | 1983-06-28 | 1985-01-17 | Hydromatik GmbH, 7915 Elchingen | Regelvorrichtung fuer mehrere aus hydrostatischen getrieben bestehende antriebsaggregate |
EP0561153A1 (de) * | 1992-03-19 | 1993-09-22 | Brueninghaus Hydromatik Gmbh | Vorrichtung zur Leistungregelung von wenigstens zwei hydrostatischen Verstellpumpen |
EP0924427A1 (de) * | 1997-12-18 | 1999-06-23 | Brueninghaus Hydromatik Gmbh | Leistungsregelventil |
EP0939225A2 (de) * | 1998-02-26 | 1999-09-01 | Brueninghaus Hydromatik Gmbh | Leistungsregeleinrichtung für mehrere verstellbare Hydropumpen |
Also Published As
Publication number | Publication date |
---|---|
DE10151401A1 (de) | 2003-05-08 |
EP1683969A1 (de) | 2006-07-26 |
EP1304482A3 (de) | 2005-09-07 |
DE50207984D1 (de) | 2006-10-12 |
EP1304482B1 (de) | 2006-08-30 |
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