EP0402871B1 - Regeleinrichtung für eine verstellbare Pumpe - Google Patents

Regeleinrichtung für eine verstellbare Pumpe Download PDF

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Publication number
EP0402871B1
EP0402871B1 EP90111124A EP90111124A EP0402871B1 EP 0402871 B1 EP0402871 B1 EP 0402871B1 EP 90111124 A EP90111124 A EP 90111124A EP 90111124 A EP90111124 A EP 90111124A EP 0402871 B1 EP0402871 B1 EP 0402871B1
Authority
EP
European Patent Office
Prior art keywords
slide
control
pressure
regulation
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
EP90111124A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0402871A3 (de
EP0402871A2 (de
Inventor
Werner Dipl.-Ing. Hörmann
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 EP0402871A2 publication Critical patent/EP0402871A2/de
Publication of EP0402871A3 publication Critical patent/EP0402871A3/de
Application granted granted Critical
Publication of EP0402871B1 publication Critical patent/EP0402871B1/de
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
    • F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
    • F04B1/12—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinder axes coaxial with, or parallel or inclined to, main shaft axis
    • F04B1/26—Control
    • 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 control device according to the preamble of claim 1.
  • Such a control device with a control valve, in which a power controller and a pressure controller are integrated, is known for example from DE-OS 19 11 695 and described below with reference to the exemplary basic circuit shown in FIG. 1, the power and pressure controllers being simplified Representation are drawn separately from each other.
  • the control device generally designated 1, comprises a control valve 10 with a power controller 2 and a pressure controller 3 superimposed by the latter, both of which regulate the hydraulic action on an adjusting cylinder 4, which is part of an adjusting device 5 for a pump 6 used in an open circuit.
  • the pump 6 driven by a drive shaft 7 sucks through a suction line 8 from a tank 9 and delivers into a working line 11.
  • a leak line 12 leading from the pump 6 to the tank 9 is shown with broken lines.
  • the power valve 13 of the power regulator 2 and the pressure limiting valve 14 of the pressure regulator 3 are arranged in a parallel arrangement in a line connecting the working line 11 to the adjusting cylinder 4.
  • the working spaces 16, 21 present on both sides of the piston 15 of the adjusting cylinder 4 can be acted upon.
  • the piston annulus 16 is connected to the working line 11 by a hydraulic line 17. Extends from the piston annulus 16 Line section 18 to the power valve 13.
  • the line extension 19 which follows the power valve 13 extends to the piston chamber 21 of the adjusting cylinder 4.
  • a branch line 23 leading to the tank 9 branches off from the line extension 19 and contains a throttle 24, the function of which is still described becomes.
  • the pressure relief valve 14 is located in a parallel line 25 branching off from the line section 18.
  • the valve spool 26 of the pressure relief valve 14 can be acted upon by the working pressure through a line section 27 and is adjustable against a spring 28 of variable spring force.
  • the line section 27 branches off from the parallel line 25 or the line section 18 and
  • the valve slide 29 of the power valve 13 is adjustable depending on the delivery rate setting of the pump 6 and depending on the working pressure against springs 31 and 31.1, possibly variable spring force.
  • an angle lever 32 mounted on its apex, one lever arm adjusts the valve slide 29 and the other lever arm is adjusted by a hydraulic piston 33, which is displaceably mounted in the transverse arrangement in the piston rod 34 of the adjusting cylinder 4 and by a connecting line 35 extending in the piston rod 34 from the piston ring space 16 to the piston 33 can be acted upon by the working pressure.
  • control device 1 The function of the control device 1 is as follows. The arrangement shown shows the depressurized state. If a consumer in the working line 11 causes an increasing working pressure A, the valve spool 29 of the power valve 13 is displaced to the left by the piston 33 and the angle lever 32 in FIG. 1, the valve spool 29 at the first passage denoted by 41 a control pressure R im Line extension 19 sets with increasing Working pressure A increases and displaces the piston 15 for the purpose of reducing the setting of the delivery volume of the pump 6, in the present exemplary embodiment pushes out.
  • the pressure regulator 3 comes into operation, which adjusts a control pressure R 1 at the second passage designated 42 in the pressure relief valve 14, which adjusts itself in a line section 36 connecting the pressure relief valve 14 to the power valve 13 and over reproduces a third passage 43 in the power valve 13 in the line extension 19 and thus in the piston chamber 21 and adjusts the pump 6 so that the working pressure A does not increase any further.
  • the piston 15 is pushed back, here pushed in, the amount of liquid displaced from the piston chamber 21 through the second passage 43 and a fourth passage 45 in the pressure limiting valve 14 connecting the line section 36 to a drain line 44 leading to the tank 9 can flow to the tank 9.
  • the power valve 13 and the pressure relief valve 14 are each formed by a 3/2-way proportional valve.
  • the invention has for its object to design a control device of the type mentioned in such a way that the flow loss required for dynamic stability can be reduced.
  • the throttled drain line ensuring the dynamic stability of the pressure regulator is controlled as a function of the function of the pressure regulator, wherein it is opened or comes into operation when the pressure regulator responds.
  • the leakage flow is thus limited to the control range of the pressure regulator, whereby a significant increase in performance is achieved because in the control range of the power regulator, the throttled drain line is inoperative and the power loss caused by the loss flow is therefore eliminated.
  • the control device uses a throttled drain line arranged in its control valve 51, which is designed in the form of a bypass 92, 89, 93 with a throttle 47.
  • the throttled bypass 92, 89, 93 of the control valve 51 according to the invention is in the latter Capacity control area closed and only functional in its pressure control area.
  • the control valve 51 comprises a valve spool 52 and a control spool 73.
  • the former corresponds to the valve spool 29 and the latter to the valve spool 26 of the known control valve 10.
  • the valve spool 52 is sleeve-shaped and is axially displaceably mounted in a housing wall 53 of the pump housing 54 and is accessible from the outside in the narrower section 55 of a stepped bore 56, the larger step of which is designated 57 and has an internal thread, into which a closure cap 58 with an adjusting device 59 for the basic setting of the control valve 51 is screwed.
  • the narrower section 55 of the stepped bore 56 cuts 53 channels in the housing wall, of which the channel labeled 61 corresponds to the line 18 according to FIG. 1 and thus contains the working pressure A.
  • the middle channel 62 corresponds to the line 19 in FIG. 1, which contains the regulating pressure R with which the piston chamber 21 of the adjusting cylinder 4 is acted upon.
  • the channel 63 arranged to the right of the channel 62 in FIGS. 2 and 3 corresponds to the drain line 44 leading to the tank according to FIG. 1.
  • the channel 61 is connected to a circumferential groove 65 on the valve slide 52, the right boundary edge of which forms a control edge 66 which interacts with a counter-control edge 67 formed by the wall of the channel 62.
  • the control edge 66 is at the same time the left boundary edge of a circumferential web 68 formed on the valve slide 52, the right boundary edge of which forms a further control edge 69 which is the left shoulder of a second initial groove 71 of the valve slide 52, which is connected to the channel 63.
  • the control edges 66, 69 interact with the mutually opposite peripheral sections 67 of the channel 62.
  • the valve slide 52 has an axial guide bore 72, in which the control slide 73 is axially displaceably mounted. At its left end in FIGS. 2 and 3, the control slide 73 has an axial blind bore from which a pressure pin 74 protrudes and is connected to the one lever arm 75 of the angle lever 76, which is pivotably mounted about an axis of rotation 77 extending transversely to the valve slide 52 .
  • the other rebel arm 78 of the angle lever 76 is acted upon by an adjustable compression spring 79 against an actuator in the form of a hydraulic piston 81, which corresponds to the piston 33 according to FIG.
  • the circumferential groove 65 is connected by a radial channel 82 to a circumferential groove 84 in the control slide 73, which is delimited on its right side by an annular shoulder 85 of the control slide 73.
  • a hydraulic working chamber 86 which is delimited on the right side by a guide section 87 which guides a narrowed guide part 88 of the control slide 73 in a sliding guide.
  • a circumferential groove 89 is formed, the left shoulder of which forms a control edge 91 which can close or open one or more ring and / or radial channels 92 in the valve slide 52 in the region of the circumferential web 68, in which throttles can be arranged, and which communicate with the circumferential groove 89 in the open position.
  • the radial channel 93 with the throttle 47 is arranged, which connects the circumferential groove 71 with the circumferential groove 89 of the valve slide 52.
  • the annular shoulder 85 is a circumferential groove 84 with the Throttle point 80 connecting working chamber 86 is provided, which is formed here by a flattening.
  • a delivery rate control is implemented in which the control or regulating pressure R is increased as the working pressure A increases.
  • the size of the working surface of the working annular chamber 86 is so dimensioned or matched to the existing arrangement that in the power control range of the control valve 51 the angle lever 76 and the set force of the compression spring 79 are the hydraulic thrust forces which move the control slide 73 relative to the valve slide 52 to the left tries to push, press over so that the control slide 73 assumes the right end position or rest position shown in FIG. 2, in which the control slide 73 rests against the bottom 72.1 of the guide bore 72.
  • the control slide 73 presses the angle lever 76, the control slide 73 being moved relative to the valve slide 52 to the left into the control position shown in FIG. 3, in which the control edge 91 controls the radial channels 92 at least partially opens and the bypass 46 formed by the radial channels 92, the circumferential groove 89 and the radial channel 93 and the throttle 47 is opened and thus a small amount of the hydraulic medium can flow away, whereby the desired dynamic stability of the control valve 51 is achieved.
  • the adjusting device 59 and also an adjusting device, generally designated 94, for the force of the compression spring 79 is designed in a manner known per se with adjusting screws which act against spring plates and adjust different spring forces by longitudinal adjustment.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Reciprocating Pumps (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP90111124A 1989-06-12 1990-06-12 Regeleinrichtung für eine verstellbare Pumpe Expired - Lifetime EP0402871B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3919175 1989-06-12
DE3919175A DE3919175A1 (de) 1989-06-12 1989-06-12 Regeleinrichtung fuer eine verstellbare pumpe

Publications (3)

Publication Number Publication Date
EP0402871A2 EP0402871A2 (de) 1990-12-19
EP0402871A3 EP0402871A3 (de) 1992-09-02
EP0402871B1 true EP0402871B1 (de) 1996-04-17

Family

ID=6382606

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90111124A Expired - Lifetime EP0402871B1 (de) 1989-06-12 1990-06-12 Regeleinrichtung für eine verstellbare Pumpe

Country Status (2)

Country Link
EP (1) EP0402871B1 (un)
DE (2) DE3919175A1 (un)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019112554A1 (en) * 2017-12-04 2019-06-13 Halliburton Energy Services, Inc. Safety pressure limiting system and method for positive displacement pumps with optional automatic restart
DE102018216831A1 (de) * 2018-10-01 2020-04-02 Robert Bosch Gmbh Regelvorrichtung für Pumpendruck und -volumenstrom mit konzentrischen Steuerschiebern

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4208925C1 (un) * 1992-03-19 1993-06-03 Hydromatik Gmbh, 7915 Elchingen, De
DE4417962A1 (de) * 1994-05-21 1995-11-23 Rexroth Mannesmann Gmbh Steueranordnung für wenigstens zwei hydraulische Verbraucher
DE19756600C1 (de) * 1997-12-18 1999-08-26 Brueninghaus Hydromatik Gmbh Leistungsregelventil
DE10358727B3 (de) 2003-12-15 2005-08-25 Brueninghaus Hydromatik Gmbh Summenleistungsregelvorrichtung
DE102011108285A1 (de) * 2010-12-22 2012-06-28 Robert Bosch Gmbh Hydraulischer Antrieb
CN114135458A (zh) * 2021-11-30 2022-03-04 力源液压（苏州）有限公司 柱塞泵恒功率控制结构

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1922145A1 (de) * 1969-04-25 1970-10-29 Bellows Valvair Kaemper Gmbh Kombinationsregler
DE1911695A1 (de) * 1969-03-03 1970-11-19 Mannesmann Meer Ag Leistungsregler fuer Hydraulikpumpen oder -motoren
DE2349124A1 (de) * 1973-09-29 1975-04-03 Rexroth Gmbh G L Hydraulische verdraengerpumpe mit druckregelung
DE2516765A1 (de) * 1975-04-16 1976-10-21 Rexroth Gmbh G L Regelbare fluegelzellenpumpe
DE3644769A1 (de) * 1986-12-30 1988-07-14 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer eine verstellbare hydrostatische maschine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1911695A1 (de) * 1969-03-03 1970-11-19 Mannesmann Meer Ag Leistungsregler fuer Hydraulikpumpen oder -motoren
DE1922145A1 (de) * 1969-04-25 1970-10-29 Bellows Valvair Kaemper Gmbh Kombinationsregler
DE2349124A1 (de) * 1973-09-29 1975-04-03 Rexroth Gmbh G L Hydraulische verdraengerpumpe mit druckregelung
DE2516765A1 (de) * 1975-04-16 1976-10-21 Rexroth Gmbh G L Regelbare fluegelzellenpumpe
DE3644769A1 (de) * 1986-12-30 1988-07-14 Brueninghaus Hydraulik Gmbh Regeleinrichtung fuer eine verstellbare hydrostatische maschine

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019112554A1 (en) * 2017-12-04 2019-06-13 Halliburton Energy Services, Inc. Safety pressure limiting system and method for positive displacement pumps with optional automatic restart
US11346336B2 (en) 2017-12-04 2022-05-31 Halliburton Energy Services, Inc. Safety pressure limiting system and method for positive displacement pumps with optional automatic restart
DE102018216831A1 (de) * 2018-10-01 2020-04-02 Robert Bosch Gmbh Regelvorrichtung für Pumpendruck und -volumenstrom mit konzentrischen Steuerschiebern
US11353120B2 (en) 2018-10-01 2022-06-07 Robert Bosch Gmbh Regulating device for pump pressure and pump volumetric flow rate, having concentric control slide valves

Also Published As

Publication number Publication date
DE59010287D1 (de) 1996-05-23
DE3919175C2 (un) 1993-01-07
EP0402871A3 (de) 1992-09-02
EP0402871A2 (de) 1990-12-19
DE3919175A1 (de) 1990-12-13

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