EP0972939B1 - Dispositif de contrôle de puissance pour plusieurs pompes hydrauliques - Google Patents

Dispositif de contrôle de puissance pour plusieurs pompes hydrauliques Download PDF

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Publication number
EP0972939B1
EP0972939B1 EP19990113343 EP99113343A EP0972939B1 EP 0972939 B1 EP0972939 B1 EP 0972939B1 EP 19990113343 EP19990113343 EP 19990113343 EP 99113343 A EP99113343 A EP 99113343A EP 0972939 B1 EP0972939 B1 EP 0972939B1
Authority
EP
European Patent Office
Prior art keywords
control device
throttle
pressure
hydraulic pump
valve
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
EP19990113343
Other languages
German (de)
English (en)
Other versions
EP0972939A2 (fr
EP0972939A3 (fr
Inventor
Dieter Dittmann
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
Publication of EP0972939A2 publication Critical patent/EP0972939A2/fr
Publication of EP0972939A3 publication Critical patent/EP0972939A3/fr
Application granted granted Critical
Publication of EP0972939B1 publication Critical patent/EP0972939B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1205—Position of a non-rotating inclined plate
    • F04B2201/12051—Angular position
    • 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
    • F04B2205/16—Opening or closing of a valve in a 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
    • F04B2205/17—Opening width of a throttling device
    • F04B2205/172—Opening width of a throttling device after the pump outlet

Definitions

  • the invention relates to a power control device for controlling the hydraulic power of a hydraulic pump whose pivot angle is adjustable by means of an adjusting device.
  • a power control device is known for example from DE 196 26 793 C1.
  • a hydraulic control device is described, which in each case comprises a power control device for two parallel hydraulic pumps.
  • the two power control devices are controlled by a pressure control device common to the hydraulic pumps.
  • the known power control devices each include a so-called hyperbola regulator, which acts back on a proportional valve acting as a power control valve via a pivoting lever.
  • a proportional valve acting as a power control valve via a pivoting lever.
  • acts on the pivot lever a proportional to the working pressure in the hydropump working line a force that causes a variable lever via a variable torque.
  • the lever travel depends on the position of an actuating piston of the adjusting device of the hydraulic pump and thus on the adjusted delivery volume of the hydraulic pump.
  • On the proportional valve therefore acts a total of a torque that the product of the working pressure in the associated working line and the adjusted delivery volume of the hydraulic pump, d. H. the hydraulic power delivered by the hydraulic pump is proportional.
  • a disadvantage of this known construction of a power control device is the relatively complex mechanical structure by means of the pivot lever, which requires considerable design effort and is also prone to failure.
  • a power control valve which is arranged in the working line of the hydraulic pump and are not coupled to the adjusting device of the hydraulic pump.
  • This power control valve has a control slot which is geometrically shaped so that the change in the throttle cross-section as a function of the displacement of the valve body of the valve is not linear, but is determined so that the product of working pressure and throttle area is at least approximately constant.
  • a disadvantage of these power control valves is the relatively inaccurate control characteristic and the relatively high structural complexity, since the throttle cross section these power control valves must be exactly dimensioned and adjusted. The production and assembly costs are therefore considerable.
  • very high spring forces are required for the provision of the valve body at high powers, so that the return spring must be designed to be relatively large. In general, therefore, a power control with a regulating function accepting valve in the working line in practice unsatisfactory.
  • the invention is based on the finding to provide a hydraulic secondary circuit in a power control device instead of a previously used pivoting lever with variable lever arm to achieve the power control function with a flow control device which supplies the secondary circuit with a constant volumetric flow, and an outlet throttle whose throttle cross-section is adjusted by the swivel angle of the hydraulic pump and which ensures the power control function with suitable dimensioning. Since the valves and throttles realizing the performance function are not arranged in the working line, but in a secondary circuit through which only a small volume flow flows, these valves and throttles are subject to considerably less wear. Furthermore, only a small heat loss occurs, so that these valves can be designed relatively small and combined to form a common valve block. The design effort for the solution according to the invention is therefore relatively low.
  • the inventive hydraulic power control is compared to the previously known mechanical power control with an adjustable pivot lever much less susceptible to interference.
  • the flow control device which has the task to supply the secondary circuit a constant volume flow, consist of a arranged in the secondary circuit throttle and either the downstream or upstream of the throttle arranged limiting valve.
  • the limiting valve is controlled by the pressure drop across the throttle so that the opening cross-section of the limiting valve is reduced when the pressure drop across the throttle increases and, conversely, the opening cross-section of the limiting valve is increased as the pressure drop across the throttle decreases. In this way it is ensured that the pressure drop across the throttle is always kept constant, resulting in a constant volume flow.
  • the limiting valve may be formed according to claim 3, for example, as a 2/2-way valve.
  • the outlet throttle is preferably designed so that increases the throttle cross section with increasing pivot angle of the hydraulic pump, starting from the neutral position. If the power control device limits the power of the hydraulic pump to a constant maximum power, the opening cross-section of the outlet throttle according to claim 5 be designed so that the opening cross section increases in proportion to the square root of the Tanges the swing angle of the hydraulic pump.
  • the control valve may be according to claim 6, a 3/2-way valve having a first connected to the working line port, a second connected to a pressure medium tank port and an indirectly or directly connected to the adjustment of the hydraulic pump third port.
  • a pressure relief valve is arranged according to claim 7 between the control valve and the adjusting device of the hydraulic pump.
  • the valve piston of the control valve is acted upon according to claim 8 preferably by the pressure difference between the prevailing in the working line high pressure and prevailing in the secondary circuit between the flow control device and the outlet throttle secondary pressure.
  • control valve according to claim 9 is connected to the adjusting device, that the control valve with increasing pressure in the secondary circuit between the flow control device and the outlet throttle an actuating cylinder of the adjusting increasingly vented to a pressure medium tank out to increase the tilt angle of the hydraulic pump.
  • the outlet throttle is preferably arranged according to claim 10 so that it connects the secondary circuit directly with a pressure medium tank.
  • Fig. 1 shows a hydraulic circuit diagram of an embodiment of the power control device according to the invention, which is generally designated by the reference numeral 1.
  • a hydraulic pump 2 sucks the pressure medium from a pressure medium tank 4 and conveys the pressure medium in a working line 3 to which an unillustrated consumer can be connected.
  • the hydraulic pump 2 is preferably driven via a drive shaft 5 at a constant speed.
  • a generally designated by the reference numeral 6 adjusting device which has a first actuating piston 7a, a first actuating cylinder 8a, a second actuating piston 7b and a second actuating cylinder 8b.
  • the first actuating cylinder 8a is a spring 9, which acts on the adjusting device 6 of the hydraulic pump 2 in the direction of maximum delivery volume.
  • the second actuating cylinder 8b With increasing pressure in the second actuating cylinder 8b, the adjusting device 6 of the hydraulic pump 2 is pivoted back in the direction of minimum displacement volume.
  • a secondary circuit 10 branches off from the working line 3.
  • the secondary circuit 10 is supplied with a constant volume flow from the working line 3 via a flow control device, generally designated by the reference numeral 11.
  • the outlet from the secondary circuit 10 into the pressure medium tank 4 takes place via a variable outlet throttle 12.
  • the throttle cross section of the outlet throttle 12 depends on the tilt angle of the hydraulic pump 2.
  • the flow control device 11 consists in the illustrated embodiment of a limiting valve 13, which is designed as a 2/2-way valve. Downstream of the limiting valve 13 is a preferably adjustable throttle 14. Although the throttle cross-section of the throttle 14 is preferably adjustable for adjustment purposes, it is immutable during operation of the power control device 1 according to the invention.
  • the valve piston of the limiting valve 13 is acted upon by the return spring 15 in the open position.
  • the limiting valve 13 is driven by the pressure drop across the throttle 14. Therefore, when the pressure drop across the restrictor 14 increases, the flow through the restricting valve 13 decreases. Conversely, when the pressure drop across the restrictor 14 decreases, the flow through the restricting valve 13 increases.
  • this control mechanism therefore, the flow rate through the flow control device 14 is increased regardless of the prevailing in the working line 3 high pressure always adjusted to a constant value.
  • the secondary pressure prevailing in the secondary circuit 10 acts on a control valve 17.
  • the control valve 17 is formed in the embodiment as a 3/2-way valve and is governed by the pressure difference between the prevailing in the working line 3 high pressure and in the secondary circuit between the flow control device 11 and the outlet throttle 12 Secondary pressure controlled.
  • the control valve 17 has a first port 18 connected to the working line 3, a second port 19 connected to the pressure medium tank 4 and a third port 20 indirectly connected to the second actuating cylinder 8b of the adjusting device 6 via a pressure limiting valve 21. If the secondary pressure in the secondary circuit 10 increases relative to the pressure prevailing in the working line 3 high pressure, a via the pressure relief valve 21 leading connecting line 22 is increasingly vented to the pressure medium tank 4 out.
  • the pressure relief valve 21 is acted upon by the pressure prevailing in the working line 3 high pressure.
  • the pressure relief valve 21 acts on the second actuating cylinder 8b of the actuator 6 with the pressure prevailing in the working line 3 high pressure, so that the actuator 6, the hydraulic pump 2 in the direction of minimum delivery swings back.
  • the operation of the power control device 1 according to the invention is as follows:
  • the valve body of the control valve 17 is therefore due to the increased difference between the prevailing in the working line 3 and the pressure prevailing in the secondary pressure 10 side pressure shifted so that the connecting line 22 and thus the second actuating cylinder 8b are subjected to an increased control pressure.
  • the hydraulic pump 2 is therefore pivoted back in the direction of a reduced delivery volume.
  • FIG. 4 is an enlarged fragmentary view of FIG. 1.
  • the throttle cross-section A must be designed from the outlet throttle 12 so that this throttle cross-section A from is proportional to the root of the tangent of the pivoting angle ⁇ of the hydraulic pump 2.
  • FIG. 2 and 3 show a structural realization according to an embodiment of the power control device 1.
  • FIG. 2 shows a longitudinal section through the power control device 1
  • FIG. 3 shows a section along the line III-III in FIG. 2.
  • the elements of the power control device 1 are integrated in the embodiment shown in FIG. 2 in a first housing block 40 and a second housing block 41, which are screwed together by screws 42 and 43.
  • An input 44 is supplied to the pressure prevailing in the working line 3 high pressure, while a first output 45 with the pressure medium tank 4 is connectable.
  • a second output 46 is connected via the connection line 16 shown in FIG. 1 with the control valve 17.
  • the control valve 17 is not integrated in the two housing bodies 40 and 41, but arranged externally.
  • a provided in a conventional flow control device flow control valve can take over the task of the control valve 17 according to the invention.
  • the designed as a 2/2-way valve limiting valve 13 of the flow control device 11 connects. Downstream of the limiting valve 13, the throttle 14 of the limiting valve 11 is arranged.
  • a first valve chamber 47 of the restriction valve 13 is connected via a connecting line 48 to the upstream portion of the throttle 14.
  • a second valve chamber 49 of the limiting valve 13 is connected via a connecting line 50 to the downstream portion of the throttle 14.
  • the pressure gradient acts on the throttle 14, wherein the valve piston 51 is moved further in Fig. 2 to the right and thus the opening cross-section the restriction valve 13 is reduced as the pressure gradient across the throttle 14 increases.
  • the valve piston 51 is shifted in Fig. 2 to the left and the limiting valve 13 further opened when the pressure drop across the throttle 14 decreases.
  • the throttle cross-section of the throttle 14 is determined by the distance of the conical end portion 52 of the threaded pin 53 of the conical recess 54 in the first housing body 40. By turning the threaded pin 53, therefore, the throttle cross-section of the throttle 14 can be changed and fixed by means of a lock nut 55.
  • valve piston 51 of the limiting valve 13 is acted upon by means of a return spring 56 in the opening direction of the limiting valve 13.
  • variable outlet throttle 12 Downstream of the throttle 14 is the adjustable outlet throttle 12.
  • FIG. 3 shows a section along the line III-III in Fig. 2, recognize.
  • a pivoting cradle 60 or swash plate of the hydraulic pump 2 is indicated in Fig. 3.
  • the pivoting cradle 60 is rotatably connected to a pivot pin 61 which is correspondingly rotated relative to the fixed insert part 67 during pivoting of the pivoting cradle of the hydraulic pump 2.
  • the stationary insert part 67 is connected via a pin 69 with a housing part 40.
  • the pivot pin 61 has a junction region 62, an outlet region 63 and an axial bore 64, which connects the junction region 62 with the outlet region 63.
  • a connected to the first output 45 gap 65 connects.
  • a control edge 66 When turning the pivot 61, a control edge 66 is rotated so that it increasingly shuts off the gap 65 and thus increasingly narrows the throttle cross-section of the outlet throttle 12.
  • the throttle cross section of the outlet throttle 12 is proportional to the root of the tangent of the pivot angle ⁇ of the hydraulic pump 4 and the pivot 61.
  • the gap 65 for example, to be designed so that its length is perpendicular to the plane of Fig. 2 is not constant but a function of the rotation angle ⁇ .
  • the invention is not limited to the illustrated embodiment.
  • other embodiments of the outlet throttle 12 or the flow control device 11 may be used.

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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 (9)

  1. Dispositif de régulation de puissance (1) pour réguler la puissance hydraulique d'une pompe hydraulique (2) qui refoule dans une conduite de travail (3), l'angle de basculement (β) de la pompe étant réglable au moyen d'un dispositif de réglage (6), comprenant
    un dispositif de régulation de courant (11) relié à la conduite de travail (3) et admettant un courant volumétrique constant (Qzu) dans un circuit annexe (10),
    un étranglement d'évacuation (12) agencé dans le circuit annexe (10), dont la section d'étranglement (Aab) dépend de l'angle de basculement (β) de la pompe hydraulique (2), et
    une valve de commande (17) qui, lorsque la pression annexe (px) dans le circuit annexe (10) entre le dispositif de régulation de courant (11) et l'étranglement d'évacuation (12) augmente, sollicite le dispositif de réglage (6) en direction d'une augmentation de l'angle de basculement (β) de la pompe hydraulique (2),
    dans lequel un piston de valve de la valve de commande (17) est attaqué par la différence de pression entre la haute pression (pHD) qui règne dans la conduite de travail (3) et la pression annexe (px) qui règne dans le circuit annexe (10) entre le dispositif de régulation de courant (11) et l'étranglement d'évacuation (12).
  2. Dispositif de régulation de puissance selon la revendication 1,
    caractérisé en ce que
    le dispositif de régulation de courant (11) est composé d'un étranglement (14) agencé dans le circuit annexe (10) et d'une valve de limitation (13) agencée dans le circuit annexe (10) en amont ou en aval de l'étranglement (14), et la valve de limitation (13) est pilotée par la chute de pression (Δp) au niveau de l'étranglement (14).
  3. Dispositif de régulation de puissance selon la revendication 2,
    caractérisé en ce que
    la valve de limitation de pression (13) est une valve 2 voies/2 positions.
  4. Dispositif de régulation de puissance selon l'une quelconque des revendications 1 à 3,
    caractérisé en ce que
    la section d'étranglement (Aab) de l'étranglement d'évacuation (12) augmente avec l'augmentation de l'angle de basculement (β) de la pompe hydraulique (2) en partant de la position neutre.
  5. Dispositif de régulation de puissance selon la revendication 4,
    caractérisé en ce que
    le dispositif de régulation de puissance (1) limite la puissance de la pompe hydraulique (2) à une puissance maximale constante, et la section d'ouverture (Aab) de l'étranglement d'évacuation (14) est proportionnelle à la racine carrée de la tangente de l'angle de basculement (b) de la pompe hydraulique (2).
  6. Dispositif de régulation de puissance selon l'une quelconque des revendications 1 à 5,
    caractérisé en ce que
    la valve de commande (17) est une valve 3 voies/2 positions, avec un premier raccord (18) relié à la conduite de travail (3), un second raccord (19) relié à un réservoir de fluide sous pression (4), et un troisième raccord (20) relié de manière au moins indirecte au dispositif de réglage (6) de la pompe hydraulique (2).
  7. Dispositif de régulation de puissance selon l'une quelconque des revendications 1 à 6,
    caractérisé en ce que
    une valve de limitation de pression (21) est agencée entre la valve de commande (17) et le dispositif de réglage (6) de la pompe hydraulique (2).
  8. Dispositif de régulation de puissance selon l'une quelconque des revendications 1 à 7,
    caractérisé en ce que
    la valve de commande (17), lors d'une augmentation de la pression annexe (px) dans le circuit annexe (10) entre le dispositif de régulation de courant (11) et l'étranglement d'évacuation (12), laisse un cylindre de positionnement (8b) du dispositif de réglage (6) progressivement s'échapper vers un réservoir à fluide sous pression (4), afin d'augmenter l'angle de basculement (β) de la pompe hydraulique (2).
  9. Dispositif de régulation de puissance selon l'une quelconque des revendications 1 à 8,
    caractérisé en ce que
    l'étranglement d'évacuation (12) relie le circuit annexe (10) à un réservoir de fluide sous pression (4).
EP19990113343 1998-07-14 1999-07-09 Dispositif de contrôle de puissance pour plusieurs pompes hydrauliques Expired - Lifetime EP0972939B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19831587 1998-07-14
DE1998131587 DE19831587C2 (de) 1998-07-14 1998-07-14 Leistungsregelvorrichtung zur Regelung der hydraulischen Leistung einer Hydropumpe

Publications (3)

Publication Number Publication Date
EP0972939A2 EP0972939A2 (fr) 2000-01-19
EP0972939A3 EP0972939A3 (fr) 2000-08-23
EP0972939B1 true EP0972939B1 (fr) 2006-08-30

Family

ID=7874043

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19990113343 Expired - Lifetime EP0972939B1 (fr) 1998-07-14 1999-07-09 Dispositif de contrôle de puissance pour plusieurs pompes hydrauliques

Country Status (2)

Country Link
EP (1) EP0972939B1 (fr)
DE (2) DE19831587C2 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10304665A1 (de) * 2003-02-05 2004-08-19 Liebherr-Machines Bulle S.A. Antrieb mit Hydromaschine
CN104235003B (zh) * 2013-12-13 2017-03-15 江苏恒立液压科技有限公司 柱塞泵控制阀及其控制方法

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1188948B (de) * 1960-07-16 1965-03-11 Metallwerk Glockerau G M B H Arbeitsfluessigkeitsmengen-Regeleinrichtung fuer hydrostatische Pumpen und Motoren
US4348159A (en) * 1980-01-07 1982-09-07 Rexnord Inc. Convertible pump servo-valve control
DE3213958A1 (de) * 1981-08-21 1983-03-03 Robert Bosch Gmbh, 7000 Stuttgart Elektrohydraulische verstelleinrichtung fuer eine hydrostatische maschine
DE3345264A1 (de) * 1983-12-14 1985-06-27 Brueninghaus Hydraulik Gmbh, 7240 Horb Drehmomenten-regeleinrichtung fuer eine verstellbare hydropumpe
DE19626793C1 (de) * 1996-07-03 1997-06-26 Brueninghaus Hydromatik Gmbh Hydraulische Regeleinrichtung zum parallelen Regeln mehrerer hydrostatischer Verstellpumpen

Also Published As

Publication number Publication date
DE19831587A1 (de) 2000-02-24
DE19831587C2 (de) 2000-06-15
EP0972939A2 (fr) 2000-01-19
DE59913812D1 (de) 2006-10-12
EP0972939A3 (fr) 2000-08-23

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