EP0561153A1 - Dispositif de réglage de puissance pour au moins deux pompes hydrostatiques à débit variable - Google Patents

Dispositif de réglage de puissance pour au moins deux pompes hydrostatiques à débit variable Download PDF

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Publication number
EP0561153A1
EP0561153A1 EP93102076A EP93102076A EP0561153A1 EP 0561153 A1 EP0561153 A1 EP 0561153A1 EP 93102076 A EP93102076 A EP 93102076A EP 93102076 A EP93102076 A EP 93102076A EP 0561153 A1 EP0561153 A1 EP 0561153A1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
compression spring
working
piston
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP93102076A
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German (de)
English (en)
Other versions
EP0561153B1 (fr
Inventor
Werner Hörmann
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
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, Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP0561153A1 publication Critical patent/EP0561153A1/fr
Application granted granted Critical
Publication of EP0561153B1 publication Critical patent/EP0561153B1/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
    • F04B2201/1203—Power on the axis
    • 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
    • F04B2203/00—Motor parameters
    • F04B2203/02—Motor parameters of rotating electric motors
    • F04B2203/0208—Power
    • 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 device for controlling the power of at least two hydrostatic variable displacement pumps according to the preamble of claim 1.
  • the power control of this known device is a total power control , which distributes the total drive power made available by the drive motor as required between the two variable pumps. Like any power control, it is based on the principle of adjusting the delivery volume of the variable pumps depending on the first control pressure along a hyperbolic characteristic, so that the maximum drive torque or, at constant drive speed, the maximum power consumption of the variable pumps remains essentially constant over the entire working range.
  • the spring arrangements assigned to the power control valves of the known device each consist of a compression spring, the setting value of which determines the back pressure and thus the maximum power consumption of the respective variable displacement pump.
  • the back pressure is selected so that each variable pump is set to 100% total drive power. This power can be transmitted by each variable pump as long as the pressure difference acting on the assigned power control valve is equal to the set back pressure, i.e. there is no second control pressure, since the other variable pump does not require any power.
  • variable pumps each transfer 50% of the total drive power, their power consumption is limited to this value.
  • a corresponding power limitation in the form of throttle and valve devices is provided, which prevents a reduction in the power setting of the other variable pump.
  • the power restriction includes the first compression springs, the design effort of which is negligible, since they are used for the power control valves instead of the return springs that are customary in the prior art.
  • the function of the power limitation results from the setting values and the arrangement of the first and second, preferably adjustable compression springs in cooperation with the respective second control pressure.
  • the back pressure determining the maximum power consumption (100% of the total drive power) of each variable pump is divided into a first back pressure, ie the setting value of the first compression spring, and a second back pressure, ie the setting value of the second compression spring.
  • the pressure difference between the back pressure and the second control pressure is divided into a first pressure difference and a second pressure difference. Since the second control pressure only acts against the second, but not against the first pressure spring, the first pressure difference remains the same as the set value of the first pressure spring.
  • the second pressure difference between the second control pressure and the second pressure spring acting on the power control valve of each variable pump changes inversely proportional to the power consumption of the other variable displacement pump and is equal to zero if this variable displacement pump consumes the power corresponding to the setting value of the second compression spring.
  • the first control pressure is only opposed by the first pressure difference, ie the counter pressure of the first compression spring, so that the power consumption of the variable pump cannot exceed the value set with this counter pressure, ie is limited to this.
  • Both first compression springs thus determine the power settings to which both variable pumps are limited if the difference between the maximum power they take up is a minimum, for example zero when the power is limited to 50% for each variable pump.
  • a two-armed swivel lever with a first lever arm and a second lever arm is assigned to each power control valve and bears on the side opposite the first compression spring with the first lever arm, the second lever arm between a first and a second piston, which is in contact with it, the first piston is mounted displaceably in the actuating piston of the actuating device designed as an actuating cylinder perpendicular to its direction of movement and is acted upon by the first control pressure in the direction of the second lever arm, and the second piston by the second compression spring against the second control pressure is applied in the direction of the second lever arm.
  • the figure shows two hydrostatic variable displacement pumps 1 and 2, such as, for example, axial piston pumps in a swashplate design, which are in mechanical drive connection via a gear, not shown, with a drive motor, also not shown, of constant drive speed.
  • the components or devices assigned to the variable displacement pumps 1, 2 are identified below by the addition .1 or .2 to the reference symbol, if necessary.
  • Each variable pump 1, 2 is via a suction line 3 and a drain line 4 connected to a tank 5 and via one working line 6.1 or 6.2 to one or more consumers, not shown.
  • the adjusting pumps 1, 2 are each assigned an adjusting device in the form of a hydraulic adjusting cylinder 7.1 or 7.2 for adjusting their delivery volumes.
  • An actuating piston 8 is arranged displaceably in each actuating cylinder 7 and is connected via a piston rod 9 to an actuating part 10 coupled to the swash plate of the respective variable displacement pump 1 or 2.
  • Each actuating piston 8 delimits in the respective actuating cylinder 7.1 or 7.2 with its (smaller) piston ring surface a left cylinder chamber 11 and with its (larger) piston surface a right cylinder chamber 12.
  • a biasing spring 13 in the left cylinder chamber 11 acts on the actuating piston 8 in the sense of reducing the right one Cylinder chamber 12 and thus in the sense of pivoting the respective variable pump 1 or 2 to a larger delivery volume.
  • Each piston rod 9 comprises a piston rod section of smaller and a piston rod section of larger diameter.
  • the latter is designated by reference numeral 14 and molded onto the respective actuating piston 8. Its end region connected to the piston rod section of smaller diameter protrudes from the respective actuating cylinder 7.1 or 7.2 and is provided with a blind bore running perpendicular to its direction of movement, in which a piston 15.1 or 15.2, hereinafter referred to as the first piston, is slidably mounted.
  • Each first piston 15.1, 15.2 can be acted upon by a control pressure corresponding to the working pressure in the working line 6.1 or 6.2 of the respective variable pump 1 or 2, hereinafter referred to as the first control pressure.
  • a first control pressure line 16.1, 17.1 or 16.2, 17.2 is provided, each consisting of a first line section 16.1 or 16.2 and a second line section 17.1 or 17.2.
  • the first line section 16.1 or 16.2 connects the working line 6.1 or 6.2 to the left cylinder space 11 of the respective actuating cylinder 7.1 or 7.2.
  • the respective left cylinder chamber 11.1 or 11.2 is connected to the respective blind bore via the second line section 17.1 or 17.2 running in the respective piston rod section 14.1 or 14.2.
  • Each first line section 16.1, 16.2 feeds the working pressure in the respective working line 6.1 or 6.2 as signal pressure to the left cylinder space 11 of the respective actuating cylinder 7.1 or 7.2 and thus serves as a signal pressure line.
  • the right cylinder spaces 12 can also be acted upon with the working pressure as a control pressure via a connection.
  • Each variable pump 1, 2 is assigned a power control valve 18.1 or 18.2 in the form of a throttling 3/2-way valve, each with a slide 19 for regulating the actuating pressure of the respective actuating cylinder 7.1 or 7.2.
  • Each power control valve 18.1, 18.2 is provided with a tank connection and a connection to a third line section 20.1 or 20.2 and a fourth line section 21.1 or 21.2, both of which serve as signal pressure lines.
  • Each third line section 20 leads to the left cylinder chamber 11 and every fourth line section 21 to the signal pressure connection of the right cylinder chamber 12 of the respective actuating cylinder 7.1 or 7.2.
  • each power control valve 18.1 or 18.2 is acted upon on the left side in the figure by an adjustable first compression spring 22 in the direction of the starting position shown, in which the tank connection is open and the connection to the third line section 20 is closed.
  • each output control valve 18.1 or 18.2 opposite the first compression spring 22 Arranged on the side of each output control valve 18.1 or 18.2 opposite the first compression spring 22 is a two-armed pivot lever with a first lever arm 23.1 or 23.2 and a second lever arm 24.1 or 24.2 which can be pivoted about a pivot bearing 32.1 or 32.2.
  • the first lever arm 23 bears against the slide 19 of the respective power control valve 18.1 or 18.2.
  • the second lever arm 24 is arranged between the first piston 15 and the piston rod 25 of a second piston 26, both of which bear against it. Therefore, the arrangement of the pistons 15, 26 relative to the second lever arm 24 is such that the first control pressure acts against the pressure of the first and second compression springs 22 and 30, respectively.
  • Every second piston 26.1, 26.2 is slidably mounted in a cylinder 27.1 or 27.2 and delimits a control chamber 28 and with its (smaller) piston ring surface its (larger) piston surface has a spring chamber 29 in which an adjustable second compression spring 30 is arranged.
  • the control rooms 28.1, 28.2 of the cylinders 27.1 and 27.2 assigned to the two variable pumps 1, 2 are each connected via a second control pressure line 31.2 and 31.1, so to speak, so to speak, crosswise to the working line 6.2 and 6.1 of the respective other variable pump 2 and 1.
  • the second piston 26.1 assigned to the power control valve 18.1 of the variable pump 1 can be acted upon with the working pressure in the working line 6.2 of the variable pump 2 as a second control pressure.
  • variable displacement pumps 1, 2 in a ratio of 60/40.
  • the compression springs 22.1 and 30.2 are at 60% and the compression springs 22.2 and 30.1 at 40% of the total drive power provided by the drive motor, i.e. to a value corresponding to the quotient of 100% total drive power and max. Delivery volume of the respective variable pump.
  • the power control valves 18.1, 18.2 are in their starting position, so that both variable pumps 1, 2 are set to the maximum delivery volume.
  • variable displacement pumps are driven by the drive motor at the same and constant speed. If, for example, the variable pump 2 does not take up any power and the second control pressure accordingly has the value zero, the second pressure difference on the second piston 26.1 is equal to the set value of the second pressure spring 30.1, so that the power control valve 18.1 and thus the variable pump 1 are set to 100% power is.
  • variable pump 1 now takes up this set power and, with a corresponding load from the connected consumer, the hydraulic force of the working pressure in the working line 6.1, and thus the first control pressure, the setting force of the working pressure 6.1 via the first piston 15.1 and the pivoting lever 23.1, 24.1 exceeds two compression springs 28.1 and 30.1, the slide 19.1 of the power control valve 18.1 is shifted to the left into the control position in which the two cylinder spaces 11.1 and 12.1 of the actuating cylinder 7.1 are connected to one another are connected.
  • the working pressure in the working line 6.1 now acts as the actuating pressure on the larger piston surface of the actuating piston 8.1 and moves this to the left while pivoting the variable displacement pump 1 until there is a balance of power at the power control valve 18.1.
  • the lever length of the second lever arm 24.1 is shortened, so that the working pressure in the working line 6.1 can increase in the same ratio as the delivery volume of the variable pump 1 decreases.
  • the product of the working pressure and delivery volume is kept constant in this way, ie the variable pump 1 is regulated along a hyperbolic characteristic.
  • the working pressure in the working line 6.1 acts via the second control pressure line 31.1 as a second control pressure on the second piston 26.2 and reduces the pressure difference against the first control pressure compared to the second pressure spring 30.2 to the value zero.
  • the power control valve 18.2 and thus the variable pump 2 is now set to 40% of the total drive power in accordance with the setting value of the first compression spring 22.2.
  • variable displacement pump 2 now consumes this power of 40%, its delivery volume is reduced in the manner already described above using the variable displacement pump 1 and regulated along a hyperbolic characteristic curve when the hydraulic force of the working pressure in the working line 6.2 with a corresponding load by the connected consumer the setting force of the first compression spring exceeds 22.2.
  • the working pressure in the working line 6.2 acts via the second control pressure line 31.2 as the second control pressure on the second piston 26.1 and reduces the pressure difference against the first control pressure compared to the second pressure spring 30.1 to the value zero.
  • the power control valve 18.1 and thus the variable pump 1 is now set to 60% of the total drive power in accordance with the setting value of the first compression spring 22.1.
  • variable pumps 1, 2 transmit these set power values of 60% or 40% of the total drive power, they are limited to these values, since the power setting of each variable pump also exceeds the set value of the assigned second compression spring 30 is not reduced by the second control pressure corresponding to the power consumption of the respective other variable pump; In such a case, the piston rod 25 of the second piston 26 acted upon by the second control pressure lifts off from the second lever arm 24, so that the power setting of the respective variable pump can no longer be influenced by the power consumption of the other variable pump.
  • a higher power consumption by one of the two variable pumps is only possible if the power consumption of the other variable pump falls below the set value of the first compression spring 22 assigned to it.
EP93102076A 1992-03-19 1993-02-10 Dispositif de réglage de puissance pour au moins deux pompes hydrostatiques à débit variable Expired - Lifetime EP0561153B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4208925 1992-03-19
DE4208925A DE4208925C1 (fr) 1992-03-19 1992-03-19

Publications (2)

Publication Number Publication Date
EP0561153A1 true EP0561153A1 (fr) 1993-09-22
EP0561153B1 EP0561153B1 (fr) 1995-11-02

Family

ID=6454520

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93102076A Expired - Lifetime EP0561153B1 (fr) 1992-03-19 1993-02-10 Dispositif de réglage de puissance pour au moins deux pompes hydrostatiques à débit variable

Country Status (4)

Country Link
US (1) US5333997A (fr)
EP (1) EP0561153B1 (fr)
JP (1) JP3526885B2 (fr)
DE (2) DE4208925C1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1304482A2 (fr) * 2001-10-18 2003-04-23 Brueninghaus Hydromatik Gmbh Dispositif de réglage de la puissance totale
WO2005057011A1 (fr) * 2003-12-15 2005-06-23 Brueninghaus Hydromatik Gmbh Dispositif de regulation de puissance totale

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4405234C1 (de) * 1994-02-18 1995-04-06 Brueninghaus Hydraulik Gmbh Vorrichtung zur Summenleistungsregelung von wenigstens zwei hydrostatischen Verstellpumpen
US5584640A (en) * 1994-04-20 1996-12-17 Eaton Corporation Grain tank unloading auger drive means
DE19626793C1 (de) * 1996-07-03 1997-06-26 Brueninghaus Hydromatik Gmbh Hydraulische Regeleinrichtung zum parallelen Regeln mehrerer hydrostatischer Verstellpumpen
US6109030A (en) * 1998-02-13 2000-08-29 Sauer Inc. Apparatus and method for ganging multiple open circuit pumps
DE19808127C2 (de) 1998-02-26 1999-12-09 Brueninghaus Hydromatik Gmbh Leistungsregeleinrichtung
US11725647B2 (en) * 2021-05-18 2023-08-15 Hamilton Sundstrand Corporation On-demand dual variable displacement positive displacement pumping system

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1922269A1 (de) * 1969-04-29 1970-11-12 Bellows Valvair Kaemper Gmbh Summenleistungsregler
EP0133870A1 (fr) * 1983-06-28 1985-03-13 Hydromatik GmbH Dispositif de réglage pour plusieurs unités de transmission hydrauliques
EP0149787A2 (fr) * 1983-12-14 1985-07-31 BRUENINGHAUS HYDRAULIK GmbH Dispositif de régulation de débit pour une pompe hydraulique réglable
EP0268078A1 (fr) * 1986-11-14 1988-05-25 Hydromatik GmbH Dispositif de régulation à sommation de puissance pour au moins deux transmissions hydrostatiques

Family Cites Families (10)

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Publication number Priority date Publication date Assignee Title
GB1526085A (en) * 1975-11-04 1978-09-27 Plessey Co Ltd Hydraulic pumping arrangements
DE3044143A1 (de) * 1980-11-24 1982-06-24 Linde Ag, 6200 Wiesbaden Steuereinrichtung fuer ein hydrostatisches antriebssystem
DE3130661A1 (de) * 1981-08-03 1983-02-17 Linde Ag, 6200 Wiesbaden Hydrostatisches antriebssystem mit einer drucknetzleitung
DE3130660A1 (de) * 1981-08-03 1983-03-03 Linde Ag, 6200 Wiesbaden Steuer- und regeleinrichtung fuer eine einstellbare hydrostatische einheit
DE3513452A1 (de) * 1985-04-15 1986-10-16 Mannesmann Rexroth GmbH, 8770 Lohr Hydrauliksystem fuer die versorgung einer hydrostatischen lenkung
US4813235A (en) * 1987-06-09 1989-03-21 Deere & Company Hydraulic gain reduction circuit
DE3728207A1 (de) * 1987-08-24 1989-03-09 Rexroth Mannesmann Gmbh Ventilanordnung fuer zwei von einem gemeinsamen antrieb angetriebene leistungsgeregelte pumpen
EP0329860A1 (fr) * 1988-02-25 1989-08-30 RIVA CALZONI S.p.A. Dispositif d'alimentation et de commande de la vitesse et du couple d'un moteur hydraulique à cylindrée variable et pression constante
DE3919175A1 (de) * 1989-06-12 1990-12-13 Hydromatik Gmbh Regeleinrichtung fuer eine verstellbare pumpe
DE4025638C1 (fr) * 1990-08-13 1991-12-05 Brueninghaus Hydraulik Gmbh, 7240 Horb, De

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1922269A1 (de) * 1969-04-29 1970-11-12 Bellows Valvair Kaemper Gmbh Summenleistungsregler
EP0133870A1 (fr) * 1983-06-28 1985-03-13 Hydromatik GmbH Dispositif de réglage pour plusieurs unités de transmission hydrauliques
EP0149787A2 (fr) * 1983-12-14 1985-07-31 BRUENINGHAUS HYDRAULIK GmbH Dispositif de régulation de débit pour une pompe hydraulique réglable
EP0268078A1 (fr) * 1986-11-14 1988-05-25 Hydromatik GmbH Dispositif de régulation à sommation de puissance pour au moins deux transmissions hydrostatiques

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
FIRMENINFORMATION, MÛrz 1987, FA. MANNESMANN-REXROTH, Hydromatik, Brueninghaus Hydraulik "Verstelldoppel- pumpe A8VO Baureihe 60 RD 93010/03.87", Seiten 1-16 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1304482A2 (fr) * 2001-10-18 2003-04-23 Brueninghaus Hydromatik Gmbh Dispositif de réglage de la puissance totale
EP1304482A3 (fr) * 2001-10-18 2005-09-07 Brueninghaus Hydromatik Gmbh Dispositif de réglage de la puissance totale
WO2005057011A1 (fr) * 2003-12-15 2005-06-23 Brueninghaus Hydromatik Gmbh Dispositif de regulation de puissance totale
US7607297B2 (en) 2003-12-15 2009-10-27 Brueninghaus Hydromatik Gmbh Total power controller

Also Published As

Publication number Publication date
DE4208925C1 (fr) 1993-06-03
DE59300837D1 (de) 1995-12-07
EP0561153B1 (fr) 1995-11-02
JP3526885B2 (ja) 2004-05-17
JPH0617761A (ja) 1994-01-25
US5333997A (en) 1994-08-02

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