EP1304482B1 - Dispositif de réglage de la puissance totale - Google Patents

Dispositif de réglage de la puissance totale Download PDF

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Publication number
EP1304482B1
EP1304482B1 EP20020016036 EP02016036A EP1304482B1 EP 1304482 B1 EP1304482 B1 EP 1304482B1 EP 20020016036 EP20020016036 EP 20020016036 EP 02016036 A EP02016036 A EP 02016036A EP 1304482 B1 EP1304482 B1 EP 1304482B1
Authority
EP
European Patent Office
Prior art keywords
piston
pressure
force
measuring
control
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 - Fee Related
Application number
EP20020016036
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German (de)
English (en)
Other versions
EP1304482A2 (fr
EP1304482A3 (fr
Inventor
Reinhold Schniederjan
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Priority to EP06005942A priority Critical patent/EP1683969A1/fr
Publication of EP1304482A2 publication Critical patent/EP1304482A2/fr
Publication of EP1304482A3 publication Critical patent/EP1304482A3/fr
Application granted granted Critical
Publication of EP1304482B1 publication Critical patent/EP1304482B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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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 summation power controller for controlling the total power of several hydrostatic piston engines and a pressure transmitter for generating a mean pressure for the power control.
  • Performance regulators for controlling delivery rates of a plurality of hydrostatic piston engines driven by a common drive source are known.
  • DE 33 23 278 C2 discloses a device in which a total of three hydraulic pumps are driven by a common drive machine. The pumps promote a pressure medium in each case an associated working line. At least two of the hydraulic pumps are designed to be adjustable, wherein the adjusting devices of the two hydraulic pumps are controllable together via a so-called hyperbola regulator.
  • an actuating piston which has two opposite piston surfaces, oppressed on one side with averaged from the two working lines of the hydraulic pumps to be adjusted pressure. This first piston surface is connected to the opposing second piston surface via a channel and a control valve arranged therein.
  • the pressure on the second piston area between the averaged working pressure is regulated as the maximum pressure and the tank pressure as the minimum pressure.
  • the position of the control valve depends on the average pressure of the working lines and the position of the actuating piston. It is taken into account by the position of the actuating piston of the swivel angle and thus the delivery volume of the adjustable hydraulic pumps.
  • the power consumed by the third hydraulic pump is taken into account by the fact that the pressure generated in the working line by the third pump via a lever mechanism on the Control valve is transmitted and thus affects its position.
  • a pressure transmitter which is used to generate the average working line pressure, is known for example from DE 34 07 827 C2.
  • the diaphragm seal comprises a stepped piston, which is arranged axially displaceably in a valve housing. He has two equally oriented stepped piston surfaces, which are each connected to the working lines of the piston engines to be adjusted.
  • the radially outer boundaries of the stepped piston surfaces form with the valve housing in each case a variable throttle.
  • the two throttles are variable together depending on the position of the stepped piston.
  • the output side of the throttles is connected via a common feed line with a counter-piston surfaces oriented against the master piston surface.
  • each throttle has an assigned on the output side arranged check valve, which opens in the direction of the sum piston surface. The total piston area is thus supplied with pressure medium only by the respective larger pressure of the working lines.
  • the described device for controlling the total power of a plurality of hydrostatic piston machines has the disadvantage that, for the consideration of a third hydrostatic piston machine complicated tuning of the lever mechanism is required to take into account their performance. Another disadvantage is that the two variable displacement pumps are only adjustable together. The proposed arrangement is therefore only suitable for the operation of two identical hydraulic pumps in conjunction with a third hydraulic pump, which is disregarded in the control of the flow rate.
  • the diaphragm seal used also has the disadvantage that the surfaces of the stepped piston are simultaneously designed as variable throttles. This leads to the operation of the diaphragm seal cause the stepped piston surfaces to be depressed by the flowing medium.
  • a changing volume in an adjusting movement of the actuating piston can thereby large volume flows occur in the diaphragm seal. The positioning accuracy of the diaphragm seal is thus reduced.
  • EP 0 561 153 A1 shows a power control device for two variable displacement pumps, each with an adjustable pressure control device, a power control valve associated therewith, which is acted upon by a first control pressure corresponding to the working pressure of the adjusting pump to be adjusted against a pressure difference in the direction control position in which the Stelltikbeaufschlagung in Controlled direction is reduced displacement pump delivery volume along a hyperbolic control curve, wherein the pressure difference from a first control pressure counteracting spring assembly backpressure and the working pressure of the other variable displacement pump results and decreases with increase thereof from a maximum value to a minimum value.
  • the spring arrangement comprises a first and second compression spring, the first compression spring is set to a minimum value and the second compression spring to a difference between the maximum value and minimum value of the pressure difference corresponding force, and the first compression spring pressurize the power control valve with its adjusting force and the second compression spring with a decreasing force with increasing second control pressure.
  • the invention has for its object to provide a sum power control simple design for several hydrostatic piston engines, which has a common control parameters and allows the operation of hydraulic pumps of different capacities.
  • the sum of power controller according to the invention has the advantage that an individual actuator is provided for each piston engine. At the same time a common variable is used as the control parameter, which acts in common on the control characteristics of the reciprocating engines. This takes into account the performance of the other piston engines driven by the same primary engine.
  • the actual point energy is taken from the respective piston engine via the working line itself. Due to the diaphragm seal therefore only small volume flows are needed. This small volume flow does not affect the control accuracy of the diaphragm seal due to the separate arrangement of the stepped piston surfaces and the control edges.
  • the variability is increased by the additionally arranged on the hyperbola control volumetric flask. From a threshold for the averaged pressure, which may be the same or different for all reciprocating engines, the influence of a second spring is turned off, creating a second possibly other control characteristic is retrievable. A vote of the total power controller is thus possible for reciprocating engines with different maximum power.
  • FIG. 1 shows a hydraulic circuit diagram of a total power control device according to the invention, in which a prime mover 1 is connected to three hydrostatic piston machines 5, 5 'and 5 "via an output shaft 2 and a countershaft 3.
  • a prime mover 1 is connected to three hydrostatic piston machines 5, 5 'and 5 "via an output shaft 2 and a countershaft 3.
  • the hydrostatic piston machines 5, 5' and 5 '' equivalent components is omitted for ease of reference to a mention of the single-coated or double-painted reference numerals.
  • the driven by the prime mover 1 countershaft 3 is connected by means of a drive shaft 4 with the hydrostatic piston machine 5.
  • the hydrostatic piston engine 5 is designed to be adjustable in its delivery volume. From the hydrostatic piston engine 5, a suitable pressure medium is conveyed into a working line 6.
  • a hyperbola 7 which will be explained in more detail below with reference to FIG. 2 and which essentially comprises an adjusting device 8, a return device 9 and a control valve 10 and a measuring piston 11.
  • the common control parameter supplied to all three hyperbolic controllers 7, 7 'and 7 " is a pressure averaged by a pressure transmitter 12.
  • the pressure averaged by the pressure transmitter 12 is made available in an outlet pressure line 13.
  • the averaged output pressure is one of the in the working lines 6, 6 'and 6 "prevailing working pressures formed arithmetic mean.
  • About working pressure connection lines 14, 14 'and 14' ' are the working lines 6, 6' and 6 '' connected to the diaphragm seal 12.
  • the working pressure connection lines 14, 14 'and 14' ' open into a connection line 15, wherein in each working pressure connection line 14, 14' and 14 '' a check valve 16, 16 'and 16 "is arranged, which opens in the direction of the connection line 15.
  • In the Connecting line 15 prevails so that in each case the highest available pressure of the working lines 6, 6 'and 6 ".
  • the prevailing in the output pressure line 13 pressure is adjusted by a 3/2-way valve 19 so that the sum of the forces acting on the measuring surfaces 17, 17 'and 17''forces is equal to the force acting on the oppositely directed sum surface 18 force.
  • the sum area 18 is connected to the output pressure line 13 via a feedback line 22 for this purpose.
  • the measuring surfaces 17, 17 'and 17 “are respectively connected via Meß réelletechnischen 23, 23' and 23" with the corresponding working pressure connection lines 14, 14 'and 14''.
  • the 3/2-way valve 19 is arbitrarily adjustable between two end positions, with the position of the 3/2-way valve depending on the resulting force on the measuring surfaces 17, 17 'and 17' 'and the opposing total area 18 sets.
  • the 3/2-way valve In a first end position, the 3/2-way valve connects the connecting line 15 to the outlet pressure line 13.
  • the outlet pressure line 13 In the second end position, the outlet pressure line 13 is connected via a return line 20 with a tank volume 21, so that the pressure prevailing in the outlet pressure line 13 with respect to the tank volume 21st is relaxed.
  • the 3/2 way valve 19 can take any intermediate position.
  • the hydrostatic piston engine 5 is adjustable by the return device 9.
  • the adjusting device 8 has an actuating piston 25 with a control piston surface 25a, which can be pressed in a control pressure chamber 26 via a control pressure line 27 from the working line 6.
  • the actuating piston 25 is axially displaced against the force of a return spring 28.
  • the hydrostatic piston engine 5 is controlled in the direction of larger pivot angle.
  • a feedback plunger 29 displaceably mounted with respect to its longitudinal axis is arranged in the actuating piston 25. wherein an end face 31 of the feedback plunger 29 is depressed via a control pressure channel from the control pressure chamber 26.
  • the side facing away from the end face 31 of the feedback plunger 29 is in contact with an L-shaped running lever 32 which is rotatably mounted in a pivot point D and having a first leg 32a and a second leg 32b.
  • an L-shaped running lever 32 which is rotatably mounted in a pivot point D and having a first leg 32a and a second leg 32b.
  • the force generated via the reversing lever 32 on the control valve 10 is counteracted by a counterforce, which is composed of the force of a first compression spring 34 and a force of a second compression spring 35.
  • the second compression spring 35 acts on the volumetric flask 11, wherein by means of a Meßkolbenstange 36 axial forces exclusively in the thrust direction to the control valve 10 are transferable.
  • the first compression spring 34 which acts directly on the control valve, and the second compression spring 35 are made adjustable in their bias.
  • the measuring piston 11 is guided in a measuring cylinder 33 which is connected via the supply line 24 to the output pressure line 13.
  • the prevailing in the measuring cylinder 33 pressure corresponding to the average pressure of the three working lines 6, 6 'and 6' 'thus acts on a Meßkolben Design 36 and reduces the force acting on the control valve 10 axial force of the second compression spring 35th
  • the control valve 10 operates in response to the force of the bell crank 32 and the opposite resultant force between two end positions.
  • the control valve 10 connects the control pressure line 27 with a return connection line 38, which opens into the return pressure chamber 39. With the pressure prevailing in the return pressure chamber 39, the surface 40 a of a return piston 40 is depressed.
  • the control valve 10 In the second end position, a connection between the return connection line 38 and the tank volume 21 is established by the control valve 10.
  • the control valve 10 regulates the ratio of the pressures acting in the control pressure chamber 26 and the return pressure chamber 29 in dependence on the performance of the piston engine 5.
  • the reversing lever 32 is on the control valve 10 a the two compression springs 34 and 35 opposing control force generated, the power is proportional. If, for example, the pressure generated by the hydrostatic piston machine 5 increases in the working line 6, then an increased force acts on the end face 31 of the feedback tappet 29 via the actuating pressure line 27 and the actuating pressure channel 30, which acts on the point A and thus the control valve 10 in FIG Adjusted direction of its first end position. By adjusting the control valve 10 in the direction of its first end position, the control pressure line 27 is increasingly connected to the return connection line 38.
  • the influence of the second pressure spring 35 is to be continuously reduced If the averaged pressure exceeds a certain threshold value, the measuring piston rod 36 raises completely from the control valve 10 and the control force generated by the lever 32. to the control valve 10 is only the first compression spring 34 in the opposite direction. By reducing the spring force, which counteracts the control force, the pressure ratio in the control pressure chamber 26 and the return pressure chamber 39 is changed so that the hydrostatic piston engine 5 is adjusted in the direction of smaller pivot angle.
  • FIG. 3 A constructive implementation of the embodiment of the total power controller according to the invention and the pressure transmitter is shown schematically in Fig. 3.
  • the control valve 10 has a control piston 41 which, depending on the resultant force acting on it from the one hand acting regulating force and the sum of the oppositely acting force of the first compression spring 34 and acting through it on the Meßkolbenthesis 37 reduced force of the second compression spring 35th is axially displaceable.
  • a first control edge 42 and a second control edge 43 are formed on the control piston 41.
  • the two control edges 42 and 43 together with the valve housing, not shown, two jointly variable throttles. By opening the throttle formed by the first control edge 42 while the control pressure line 27 is increasingly connected to the return connection line 38.
  • connection between the return connection line 38 and the tank 21 is closed by a reduction in the cross section of the second throttle of the control edge 43. If the hydrostatic piston engine 5 is set to its minimum pivoting angle by pressing the return pressure chamber 39, the return pressure chamber 39 is connected to the tank 21 via a relief line 44 arranged in the return piston 40.
  • the pressure transmitter 12 has a two-part stepped piston 45, 46, a first stepped piston part 45 and a second stepped piston part 46.
  • the two stepped piston parts 45 and 46 are arranged displaceably in a valve body 70.
  • the three measuring surfaces 17, 17 'and 17''are equal.
  • the three measuring surfaces 17, 17 'and 17''are formed as end faces of the cross-sectional changes of the first stepped piston member 45 and oriented in the same direction.
  • the three volumes formed in front of the measuring surfaces 17, 17 'and 17' 'between the first stepped piston part 45 and the valve body 70 are each provided with a measuring pressure line 23, 23' and 23 '' and via the corresponding working pressure lines 14, 14 'and 14' '.
  • the working pressure lines 14 and 14 ' are connected to two inputs of a first shuttle valve 47.
  • the output line 49 of the shuttle valve 47 is connected to an input of a second shuttle valve 48 whose second input is connected to the working pressure line 14 ''.
  • the output of the second shuttle valve 48 is connected to the connecting line 15.
  • a first control edge 50 and a second control edge 51 are arranged by radial tapers.
  • the first and second control edge 50 and 51 forms with the valve body 70 from two common variable throttle 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 output pressure line 13 with the tank 21 is connected.
  • the enclosed by the sum piston surface 18 and the valve body 70 volume 71 is on the Feedback line 22 is connected to the output pressure line 13.
  • the first stepped piston part 45 and the second stepped piston part 46 are held on a contact surface 52 in abutment.
  • the position of the thus jointly displaceable stepped piston parts 45 and 46 is thereby adjusted so that the two stepped piston parts 45 and 46 are in equilibrium of forces.
  • a trained around the contact surface 52 space 72 in the valve body 70 is connected via a further discharge line 60 to the tank 21.
  • hydrostatic piston machines 5, 5 'and 5 " By means of the pressure transmitter 12 described and the summation power control associated therewith, it is also easily possible to operate hydrostatic piston machines 5, 5 'and 5 "with a common control parameter if the hydrostatic piston machines 5, 5' and 5" have different nominal powers
  • the performance of the hydrostatic piston engines 5, 5 'and 5' ' is preferably carried out so that the force which is generated by the first compression spring 34 and the second compression spring 35 on the control piston 41 of the control valve 10, 100% of the power of the associated hydrostatic Piston engine 5, 5 'or 5 "corresponds. If the pressure averaged in the outlet pressure line 13 by the pressure averager 12 is so great that the volumetric flask 11 lifts off from the control piston 41, then the hydrostatic piston machine 5 has a power control which is determined exclusively by the first compression spring 34.
  • the use of a divided stepped piston 45, 46 with a first stepped piston part 45 and a second stepped piston part 46 facilitates the production of the pressure transmitter 12 according to the invention considerably. Tensions as they could arise through the processing of a one-piece stepped piston during operation, are thus avoided and the control operates accordingly more accurately.
  • the total power controller according to the invention is also suitable for use in systems 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)

Claims (6)

  1. Régulateur de puissance totale pour plusieurs machines hydrostatiques (5, 5', 5 ") à pistons,
    ledit régulateur de puissance totale étant raccordé à plusieurs machines hydrostatiques à pistons dont le volume refoulé peut être ajusté au moyen de dispositifs de réglage (8, 9, 8', 9', 8", 9"), et qui refoulent un fluide pressurisé dans des conduits de travail (6, 6', 6"),
    les dispositifs de réglage (8, 9, 8', 9', 8", 9") pouvant être régulés par un dispositif de régulation hyperbolique (7, 7', 7"), et la pression de travail des machines hydrostatiques (5, 5', 5") à pistons étant délivrée à un moyenneur de pression (12),
    sachant qu'il est prévu, pour chaque dispositif de réglage (8, 9, 8', 9', 8", 9") des machines hydrostatiques (5, 5', 5") à pistons, un dispositif distinct de régulation hyperbolique (7, 7', 7") englobant un piston régulateur (41, 41', 41") et un piston mesureur (11, 11', 11"),
    ledit piston mesureur (11, 11', 11 ") étant précontraint par une force axiale qui peut être répercutée sur ledit piston régulateur (41, 41', 41") et à laquelle s'oppose une force développée, sur une surface (37, 37', 37") de piston mesureur, par une pression moyennée par ledit moyenneur de pression (12), et
    sachant que la somme de toutes les forces agissant sur le piston régulateur (41, 41', 41") dans la direction de la force axiale est égale, lorsque la surface (37, 37', 37") d'un piston mesureur est exempte de pression, à la force agissant sur ledit piston régulateur (41, 41', 41"), dans la direction opposée, en présence d'une puissance nominale de la machine hydrostatique (5, 5', 5") à piston.
  2. Régulateur de puissance totale selon la revendication 1,
    caractérisé par le fait
    qu'un ressort de pression (35, 35', 35") est prévu pour développer la force axiale agissant sur le piston mesureur (11, 11', 11").
  3. Régulateur de puissance totale selon la revendication 1 ou 2,
    caractérisé par le fait
    que les surfaces (37, 37', 37") des pistons mesureurs (11, 11', 11'') sont identiques.
  4. Régulateur de puissance totale selon la revendication 1 ou 2,
    caractérisé par le fait
    que les surfaces (37, 37', 37") des pistons mesureurs (11, 11', 11") sont différentes.
  5. Régulateur de puissance totale selon l'une des revendications 1 à 4,
    caractérisé par le fait
    que le dispositif de régulation hyperbolique (7, 7', 7") comprend un levier de renvoi (32, 32', 32") sur lequel agit un couple de rotation proportionnel au volume refoulé par la machine hydrostatique (5, 5', 5") à piston, et proportionnel à la pression régnant dans le conduit de travail (6, 6', 6"), ledit levier de renvoi (32, 32', 32") répercutant, sur le piston régulateur (41, 41', 41"), une force correspondant audit couple de rotation.
  6. Régulateur de puissance totale selon la revendication 5,
    caractérisé par le fait
    que le levier de renvoi (32, 32', 32") est monté rotatif en un point de rotation (D, D', D"), une première branche (32a, 32a', 32a") dudit levier de renvoi (32, 32', 32") étant soumise, en un point d'attaque (A, A', A"), à l'action d'une force proportionnelle à la pression régnant dans le conduit de travail (6, 6', 6") ; et par le fait que la distance comprise entre le point d'attaque (A, A', A") et le point de rotation (D, D', D") est proportionnelle à l'angle de pivotement réglé de la machine hydrostatique (5, 5', 5") à piston, une seconde branche (32b, 32b', 32b") dudit levier de renvoi (32, 32', 32") répercutant, sur le piston régulateur (41, 41', 41''), la force correspondant au couple de rotation résultant.
EP20020016036 2001-10-18 2002-07-18 Dispositif de réglage de la puissance totale Expired - Fee Related EP1304482B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP06005942A EP1683969A1 (fr) 2001-10-18 2002-07-18 Dispositif de réglage de la puissance totale

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10151401 2001-10-18
DE2001151401 DE10151401A1 (de) 2001-10-18 2001-10-18 Summenleistungsregler und Druckmittler

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP06005942A Division EP1683969A1 (fr) 2001-10-18 2002-07-18 Dispositif de réglage de la puissance totale

Publications (3)

Publication Number Publication Date
EP1304482A2 EP1304482A2 (fr) 2003-04-23
EP1304482A3 EP1304482A3 (fr) 2005-09-07
EP1304482B1 true EP1304482B1 (fr) 2006-08-30

Family

ID=7702894

Family Applications (2)

Application Number Title Priority Date Filing Date
EP20020016036 Expired - Fee Related EP1304482B1 (fr) 2001-10-18 2002-07-18 Dispositif de réglage de la puissance totale
EP06005942A Withdrawn EP1683969A1 (fr) 2001-10-18 2002-07-18 Dispositif de réglage de la puissance totale

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP06005942A Withdrawn EP1683969A1 (fr) 2001-10-18 2002-07-18 Dispositif de réglage de la puissance totale

Country Status (2)

Country Link
EP (2) EP1304482B1 (fr)
DE (2) DE10151401A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
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

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5543245A (en) * 1978-09-22 1980-03-27 Komatsu Ltd Volume controller of variable hydraulic pump
DE3217360A1 (de) * 1982-05-08 1983-11-10 Robert Bosch Gmbh, 7000 Stuttgart Regeleinrichtung fuer eine verstellbare pumpe
DE3407827C2 (de) * 1983-03-24 1985-03-28 Hydromatik GmbH, 7915 Elchingen Druckmittler
DE3323278C2 (de) * 1983-06-28 1986-05-22 Hydromatik GmbH, 7915 Elchingen Regelvorrichtung für mehrere aus hydrostatischen Getrieben bestehende Antriebsaggregate
DE3625222A1 (de) * 1986-07-25 1988-02-04 Index Werke Kg Hahn & Tessky Druckregler fuer hydraulisch gesteuerte werkzeugmaschinen
DE4208925C1 (fr) * 1992-03-19 1993-06-03 Hydromatik Gmbh, 7915 Elchingen, De
DE19735110B4 (de) * 1997-08-13 2004-09-16 Brueninghaus Hydromatik Gmbh Regelvorrichtung mit Druckmittler
DE19756600C1 (de) * 1997-12-18 1999-08-26 Brueninghaus Hydromatik Gmbh Leistungsregelventil
DE19808127C2 (de) * 1998-02-26 1999-12-09 Brueninghaus Hydromatik Gmbh Leistungsregeleinrichtung

Also Published As

Publication number Publication date
DE50207984D1 (de) 2006-10-12
EP1683969A1 (fr) 2006-07-26
DE10151401A1 (de) 2003-05-08
EP1304482A2 (fr) 2003-04-23
EP1304482A3 (fr) 2005-09-07

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