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EP1251277B1 - Système de contrôle de puissance basé sur la pression moyenne - Google Patents

Système de contrôle de puissance basé sur la pression moyenne Download PDF

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Publication number
EP1251277B1
EP1251277B1 EP20020006285 EP02006285A EP1251277B1 EP 1251277 B1 EP1251277 B1 EP 1251277B1 EP 20020006285 EP20020006285 EP 20020006285 EP 02006285 A EP02006285 A EP 02006285A EP 1251277 B1 EP1251277 B1 EP 1251277B1
Authority
EP
European Patent Office
Prior art keywords
pressure
piston
output
control
input
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
Application number
EP20020006285
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German (de)
English (en)
Other versions
EP1251277A3 (fr
EP1251277A2 (fr
Inventor
Manfred Blum
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
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Filing date
Publication date
Application filed by Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1251277A2 publication Critical patent/EP1251277A2/fr
Publication of EP1251277A3 publication Critical patent/EP1251277A3/fr
Application granted granted Critical
Publication of EP1251277B1 publication Critical patent/EP1251277B1/fr
Anticipated expiration legal-status Critical
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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

Definitions

  • the invention relates to a pressure transmitter and a power control device, in particular for controlling the total power of several hydrostatic piston machines.
  • Diaphragm seals that produce an average output pressure from two input pressures are, for. B. from DE 34 07 827 C2. They have a stepped piston, which is arranged axially displaceably in a housing.
  • the stepped piston has two stepped surfaces oriented in the same direction, which can be acted upon by an input pressure and whose radially outer boundary is formed with the housing of the diaphragm seal as a variable throttle.
  • a check valve is arranged in each case.
  • a surface oriented in the opposite direction to the step surfaces, which is equal to the sum of the two step surfaces, can be acted upon by the pressure taken from the outlet line.
  • the function of the known pressure transmitter is limited to a mere averaging of two input pressures to an output pressure which is equal to the arithmetic mean of the input pressures.
  • the diaphragm seal has no possibility of intervention, so that additional components are required for additional functionalities.
  • the construction cost increases considerably, for example by connecting various modules with pressure lines.
  • the development effort increases by matching different modules to each other. Especially disadvantageous in operation are the cumulative losses of the individual modules.
  • EP 0 897 062 A2 discloses a pressure control circuit for a plurality of hydraulic pumps.
  • the pressure control loop comprises a pressure transmitter, to which the two working pressures of a first and a second hydraulic pump are supplied. These working pressures act on the step surfaces of a valve piston, which is acted upon in the opposite direction by the averaged pressure. The sum of the two acted upon by the working pressures surfaces is equal to the area, which is acted upon by the averaged pressure.
  • a partial section through a pressure transmitter 1 is shown.
  • the diaphragm seal 1 consists of a housing 2, in which a blind bore 3 is introduced.
  • the blind bore 3 serves to receive a valve sleeve 4.
  • the valve sleeve 4 has a stepped through bore 5 extending over its entire length. In this case, the diameters of the stepped through-hole 5 decrease from the bottom of the blind bore 3 in the direction of the open end.
  • a stepped piston 6 is used, the longitudinal extent is smaller than the longitudinal extent of the valve sleeve 4.
  • the stepped piston 6 is slidable in the axial direction in the through hole 5.
  • a nozzle 7 is screwed, for example, in an expanded part of the blind bore 3, so that an inserted disc 8 with a central through hole holds the valve sleeve 4 at the bottom of the blind hole 3.
  • inlet pressure holes 9 a, 9 b are provided in the housing, which in circumferential grooves 10a, 10b open, which are outside of the valve sleeve 4 introduced.
  • the grooves 10a, 10b generate with the inner wall of the blind bore 3 a circumferential channel which is to be supplied via the inlet pressure holes 9a, 9b with pressure medium.
  • the circumferential grooves 10a, 10b are connected by radial bores 11a, 11b with the interior of the valve sleeve 4 formed by the stepped through-hole 5.
  • the stepped piston 6 has three sections with diameters D1, D2 and D3, each corresponding to a diameter of the stepped through-hole 5 and sealingly cooperate. Between the sections with the diameters D3 and D2 and between the sections with the diameters D2 and D1, a reduced cross section formed part of the stepped piston 6 is arranged. This results between the part of the stepped piston 6 with a reduced cross-section and the inner wall of the valve sleeve 4 each have an annular space 13a, 13b. The extent of the annular spaces 13a, 13b in the axial direction is dimensioned such that between the radial bores 11a, 11b and in each case an outlet bore 14a, 14b a flowable connection can be produced when the stepped piston 6 is in a first end position.
  • the annular spaces 13a, 13b are bounded by input step surfaces 12a, 12b.
  • the outer peripheral edges of the input step surfaces 12a, 12b simultaneously close the exit bores 14a, 14b when the stepped piston 6 moves from its first end position. It is formed a common variable throttle point.
  • the formed on the stepped piston 6 input stage surfaces 12a, 12b are each greater than the on the opposite side of the annular spaces 13a, 13b bounding surfaces of the stepped piston 6.
  • the output bores 14a, 14b open into a respective annular channel 15a, 15b.
  • the annular channels 15a, 15b are connected via a bore with a respective check valve 16a, 16b.
  • the check valves 16a, 16b have an identical structure, and consist of a pressed into the housing 2 valve seat body 17 which cooperates with a valve stem 18 to a sealing seat.
  • the valve stem 18 is acted upon axially by a valve spring 19 with a force in the direction of the valve seat body 17.
  • the valve spring 19 is supported in a valve holder 20, which is screwed into the housing 2 and sealed by an O-ring.
  • the valve tappets 18 of the check valves 16a, 16b penetrate an outlet line 21 which is widened in the region of the valve tappet 18 so that the pressure medium can flow around the valve tappet 18.
  • the pressure medium flowing from the annular spaces 13a, 13b via the throttle bores 14a, 14b and the check valves 16a, 16b into the outlet line 21 can be supplied via an outlet bore 22 for further use.
  • the output line 21 is also connected via a throttle point 23 to the tank line system 24.
  • An outlet pressure space 25, which is formed in the through hole 5 of the valve sleeve 4, is connected via a further radial bore and a circumferential groove with the output line 21.
  • the self-adjusting in the output line 21 pressure acts on an output pressure surface 26 and the end face of a stopper 27 which is arranged on the stepped piston 6.
  • the output pressure is thus set to a pressure that is reduced in relation to the arithmetic mean of the input pressures in the ratio of the sum of the input stage surfaces 12a, 12b to the output pressure surface 26.
  • the check valves 16a, 16b are designed as adjustable check valves 16a, 16b.
  • the setting can be changed, for example, by changing the Pretension of the valve spring 19 done. This will ensure that as the input pressure increases, the check valve 16a or 16b associated with the other input pressure closes, although there is also a positive pressure differential between the lower two input pressures and the output pressure at the associated check valve 16a or 16b.
  • a connecting hole 9 is introduced into the socket 7, which has an internal thread.
  • the end face 30 of the stepped piston 6 can be acted upon with a pressure which causes a force on the stepped piston 6, which is directed in the direction of the bottom of the blind bore 3.
  • the throttle bores 14a, 14b can be opened so far until the stop 27 abuts against the bottom of the blind bore 3.
  • the second exemplary embodiment has a two-part valve sleeve consisting of a first valve sleeve part 33 and a second valve sleeve part 34.
  • the second valve sleeve part 34 has an axially continuous, stepped guide recess 36, wherein the smaller radial extent of the guide recess 36 to the bottom of the blind bore 3 is oriented. In the guide recess 36 of the second step piston part 32 is inserted.
  • the second stepped piston part 32 likewise has a step, wherein the radial expansions formed in this way correspond to the radial expansions of the guide recess 36 and cooperate in a sealing manner.
  • the steps in the second stepped piston part and the guide recess 36 are offset from one another in the axial direction.
  • the thus formed output pressure chamber 25 is connected via a radial bore and a circumferential groove on the second valve sleeve part 34, as in first embodiment, connected to the output line 21.
  • a compensation bore 37 is introduced in the second stepped piston part 32, which is designed as a blind bore.
  • the second stepped piston part 32 has, on its side oriented toward the first stepped piston part 31, a peripheral shoulder 39, which is connected to the compensation bore 37 by an overflow bore 38.
  • the resulting circumferential channel is connected to the tank line system 24, for example via frontally introduced into the second valve sleeve part 34 grooves. A resulting between the bottom of the blind bore 3 and the second step piston part 32 by movement overpressure or underpressure can thus be reduced by the tank line system 24.
  • a dome-shaped contact surface 40 is formed at the first stepped piston part 31 facing end face of the second stepped piston part 32.
  • the contact surface 40 is in abutment with the end face of the first stepped piston part 31.
  • the two stepped piston parts 31 and 32 can transmit thrust forces in the axial direction.
  • the passage guide 5 is incorporated, which cooperates with the stepped first stepped piston part 31, as explained in the description of the first embodiment.
  • the stepped piston 6 can be acted upon by an oversteer force.
  • the first stepped piston member 31 is acted upon by its open end of the housing 2 towards the oriented end face by an electromagnet 41 with an overdrive force.
  • the electromagnet 41 is screwed into the connecting hole 29 of the nozzle 7, wherein from the housing of the electromagnet 41 frontally a plunger 42 protrudes, which is preferably provided with a thread, so that an adjusting sleeve 43 can be axially positioned.
  • the illustrated embodiments of the diaphragm seal 1 with a one-piece or multi-part stepped piston 6 can be combined in any way with the illustrated override options.
  • a power control device for controlling the total power of two adjustable hydrostatic piston machines is shown schematically.
  • a first and second piston engine 50, 51 are driven by a respective first and second drive shaft 52, 53.
  • the adjustable in their flow volume first and second piston engine 50, 51 promote a pressure medium in a first and second working line 54, 55.
  • the required for building a power control device according to the invention identical components for the first and second piston engine 50, 51 are based on their interaction be explained with the first piston machine 50. Only the components on the first piston machine 50 are explained, the reference numerals are provided with a.
  • the components on the second piston engine 51 are identical and the reference numerals are provided with b.
  • an adjusting device 56a For adjusting the delivery volume of the first piston engine 50, an adjusting device 56a is provided.
  • the adjusting device 56 a has an actuating piston 60 a, which at two oppositely disposed piston surfaces with a in a control pressure chamber 58a or a pressure prevailing in an operating pressure chamber 59a pressure is acted upon.
  • the effective piston area in the control pressure chamber 58a is greater than the effective piston area in the operating pressure chamber 59a.
  • the operating pressure chamber 59a is connected via a line system to the first working line 54.
  • the signal pressure chamber 58a is connected via a line to a terminal of a control valve 57a, which connects the working pressure line 54a with the control pressure chamber 58 in a first end position.
  • the self-adjusting pressure equilibrium in the operating pressure chamber 59a and the control pressure chamber 58a generates due to the larger-acting piston surface in the control pressure chamber 58a, a force that adjusts the control piston 60a and thus the first piston engine 50 in the direction of a reduced delivery volume.
  • the movement of the actuating piston 60a is transmitted via a connecting device 61a to the control valve 57a.
  • the control valve 57a is acted upon by the connecting device 61a in the direction of its second end position with a force.
  • the connecting line of the control pressure chamber 58a is connected to the tank line system 24a.
  • the control valve 57a is biased by a setting spring 69a.
  • the control valve 57a is acted upon by a hydraulic control member 62a with a force.
  • the hydraulic control member 62a consists of a control piston 63a, which is acted upon on both sides with a pressure.
  • the control piston 63a is biased with an adjustable spring in a spring chamber 64a so with a force that the force of the adjusting spring 69a is compensated by the spring in the spring chamber 64a and the control valve 57a is in a defined starting position.
  • the spring chamber 64a is connected to the output line 21 of the diaphragm seal 1.
  • the pressure transmitter 1 is hydraulically overridden and with an override pressure line 65th connected.
  • the inlet pressure bores 9a, 9b of the diaphragm seal 1 are connected to the first working line 54 and the second working line 55 via a first inlet pressure line 66 and a second inlet pressure line 67.
  • the control piston 63a is acted upon in the spring chamber 64a with the outlet pressure prevailing in the outlet line 21, which is proportional to the mean pressure of the first and second working lines 64, 55. Increases in the first and / or second working line 54, 55, the pressure, this also leads to an increase in pressure in the output line 21.
  • the acting in the spring chamber 64a on the control piston 62a increased pressure generates a force on the control valve 57a in the direction of first end position, so that the pressure in the control pressure chamber 58 a, the pressure in the first working line 54 is approximated. According to the above description, this results in an adjustment of the first piston engine 50 towards lower delivery volume.
  • the above-described adjustment to smaller delivery volume takes place in an analogous manner in the second piston engine 51.
  • the pressure transmitter 1 can be overridden via the overpressure pressure line 65 so that the throttles on the input step surfaces 12a, 12b are opened by the displacement of the stepped piston 6 and the pressure in the outlet line 21 is rising.
  • the piston engines 50, 51 are adjusted in the direction of minimum delivery volume. Contrary to the force acting on the control piston 63 a, generated in the spring chamber 64 a force, the piston can by a second control pressure line 68 a with a second control pressure to be applied. As a result, the starting position for the power control device is adjustable.
  • FIG. 4 shows a power control device which has a pressure transmitter with an electromagnetic override device 70.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Sealing Devices (AREA)
  • Control Of Fluid Pressure (AREA)

Claims (8)

  1. Dispositif de moyennage de pression pour préparer une pression de sortie moyennée à partir de deux pressions d'entrée, comprenant un piston étagé (6) agencé en translation dans un boîtier (2) et présentant au moins deux surfaces de gradins d'entrée (12a, 12b) orientées dans le même sens, surfaces qui peuvent être chacune sollicitée par l'une des pressions d'entrée et dont les périphéries extérieures sont réalisées comme arêtes de commande d'étranglements variables communs, et comprenant au moins deux clapets antiretour (16a, 16b) qui sont agencés chacun dans une conduite de liaison qui va respectivement de l'étranglement variable à une conduite de sortie (21), et une surface de pression de sortie (26) réalisée sur le piston étagé (6), orientée en sens opposé aux surfaces de gradins d'entrée (12a, 12b), surface qui peut être sollicitée par la pression de sortie, caractérisé en ce que, pour générer une pression de sortie réduite, la surface de pression de sortie (26) est supérieure à la somme des surfaces de gradins d'entrée (12a, 12b).
  2. Dispositif de moyennage de pression selon la revendication 1, caractérisé en ce que le piston étagé (6) est constitué d'une première partie de piston étagé (31) et d'une seconde partie de piston étagé (32), et en ce que des forces de poussée axiale sont susceptibles d'être transmises depuis l'une des parties de piston étagé (31 ; 32) à l'autre partie de piston étagé (32 ; 31).
  3. Dispositif de moyennage de pression selon la revendication 2, caractérisé en ce que les surfaces de gradins d'entrée (12a, 12b) sont agencées sur la première partie de piston étagé (31), et en ce que la surface de pression de sortie (26) est agencée sur la seconde partie de piston étagé (32).
  4. Dispositif de moyennage de pression selon l'une des revendications 1 à 3, caractérisé en ce qu'une force de surrégulation agissant dans le même sens que la force générée au niveau des surfaces de gradins d'entrée (12a, 12b) est susceptible d'être générée au niveau d'une surface frontale (30) agencée à l'opposé de la surface de pression de sortie (26).
  5. Dispositif de moyennage de pression selon la revendication 4, caractérisé en ce que la force de surrégulation sur le piston étagé (6) est susceptible d'être générée de façon hydraulique par une pression sur la surface frontale (30).
  6. Dispositif de moyennage de pression selon la revendication 4, caractérisé en ce que la force de surrégulation sur le piston étagé (6) est susceptible d'être transmise à la surface frontale (30) par un poussoir (42, 43) d'un électroaimant (41).
  7. Dispositif de régulation de puissance pour réguler la somme des puissances d'au moins deux machines hydrostatiques à pistons (50, 51), dont les volumes au refoulement sont réglables par une pression de réglage respective au moyen d'un dispositif de réglage hydraulique respectif (56a, 56b), la pression de réglage pour les dispositifs de réglage (56a, 56b) pouvant être régulée par une valve de régulation respective (57a, 57b), caractérisé en ce que, pour piloter les valves de régulation (57a, 57b), il est prévu un organe de commande hydraulique respectif (62a, 62b), dont la pression de commande commune est générée par un dispositif de moyennage de pression commun (1) selon l'une des revendications 1 à 6, et ladite pression de commande est une pression de sortie moyennée est réduite à partir des pressions de service des machines à pistons (50, 51).
  8. Dispositif de régulation de puissance selon la revendication 7, caractérisé en ce qu'un piston de commande respectif (63a, 63b) de chaque organe de commande hydraulique (62a, 62b) est susceptible d'être attaqué par une seconde pression de commande dont la force a un effet opposé à la pression de commande.
EP20020006285 2001-04-19 2002-03-20 Système de contrôle de puissance basé sur la pression moyenne Expired - Lifetime EP1251277B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10119237 2001-04-19
DE2001119237 DE10119237B4 (de) 2001-04-19 2001-04-19 Druckmittler

Publications (3)

Publication Number Publication Date
EP1251277A2 EP1251277A2 (fr) 2002-10-23
EP1251277A3 EP1251277A3 (fr) 2004-03-31
EP1251277B1 true EP1251277B1 (fr) 2006-09-13

Family

ID=7681999

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20020006285 Expired - Lifetime EP1251277B1 (fr) 2001-04-19 2002-03-20 Système de contrôle de puissance basé sur la pression moyenne

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Country Link
EP (1) EP1251277B1 (fr)
DE (2) DE10119237B4 (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10134747B4 (de) * 2001-07-17 2017-05-04 Liebherr-Machines Bulle S.A. Verfahren und Vorrichtung zur lastabhängigen Steuerung der Fluidversorgung eines Fluidkreises
DE102006055931B4 (de) * 2006-11-27 2011-07-28 Robert Bosch GmbH, 70469 Hydrostatischer Antrieb mit einer Summenleistungsregelvorrichtung
DE102008031768A1 (de) * 2008-07-04 2010-01-07 Alpha Fluid Hydrauliksysteme Müller GmbH Regelanordnung für proportionale Winkelverstellung

Family Cites Families (6)

* 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
JPS59217066A (ja) * 1983-03-24 1984-12-07 ハイドロマチツク・ゲゼルシヤフト・ミツト・ベシユレンクタ−・ハフツング 圧力アベレ−ジヤ−
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
DE19626793C1 (de) * 1996-07-03 1997-06-26 Brueninghaus Hydromatik Gmbh Hydraulische Regeleinrichtung zum parallelen Regeln mehrerer hydrostatischer Verstellpumpen
DE19735110B4 (de) * 1997-08-13 2004-09-16 Brueninghaus Hydromatik Gmbh Regelvorrichtung mit Druckmittler

Also Published As

Publication number Publication date
EP1251277A3 (fr) 2004-03-31
DE50208102D1 (de) 2006-10-26
EP1251277A2 (fr) 2002-10-23
DE10119237A1 (de) 2002-10-31
DE10119237B4 (de) 2005-08-11

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