EP0832360A1 - Elektrohydraulisch verstellbare pumpe - Google Patents
Elektrohydraulisch verstellbare pumpeInfo
- Publication number
- EP0832360A1 EP0832360A1 EP95913049A EP95913049A EP0832360A1 EP 0832360 A1 EP0832360 A1 EP 0832360A1 EP 95913049 A EP95913049 A EP 95913049A EP 95913049 A EP95913049 A EP 95913049A EP 0832360 A1 EP0832360 A1 EP 0832360A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- signal
- control
- actual value
- control 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.)
- Granted
Links
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
- F04B49/06—Control using electricity
-
- 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
- F04B11/00—Equalisation of pulses, e.g. by use of air vessels; Counteracting cavitation
-
- 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
- F04B2201/08—Cylinder or housing parameters
- F04B2201/0804—Noise
-
- 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
-
- 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
Definitions
- the invention relates to an electrohydraulically adjustable pump according to the preamble of the main claim.
- Such pumps in particular axial, radial or
- Vane pumps are known in many embodiments and are used in a variety of different areas of application of hydraulics.
- the main advantages of the electro-hydraulic adjustment of these pumps are the quick and precise electrical controllability and the loss ar ⁇ nut of the drives built with them due to the lack of complex valves between the pump and the consumer.
- the adjusting pistons of the pumps are pressurized with pressure medium via a control valve.
- the size relevant for pump adjustment or swiveling, the eccentricity of the cam ring for radial piston pumps and vane pumps or the swivel angle of the swash plate for axial piston pumps is measured with a displacement transducer.
- This actual value signal of the displacement transducer which is proportional to the pump delivery quantity, is fed to an electronic control amplifier and compared there with the pending setpoint.
- the actual value of the valve adjustment is fed to this control amplifier, which controls the control valve, via a displacement transducer.
- the control valve or the pump can be controlled via an internal pressure supply or via an external pressure supply.
- the adjusting element for example cam ring or swash plate
- the noise development increases with the falling rigidity of the hydraulic clamping of the adjusting element and is caused by the parts of the engine forces acting in the direction of the adjustment.
- this leads to a more or less strong deflection of the entire engine in time with the pistons or chambers entering or exiting the pressure chamber of the pump.
- the additional pulse-shaped control signal is advantageously formed via a speed signal, which is obtained by a conventional speed sensor on the pump.
- This speed sensor detects the passage of the pump pistons or vanes and generates a corresponding signal.
- This signal is fed in the form of a trigger signal to a signal converter, which is based on a stored characteristic or a stored characteristic field converts the trigger signal into an additional signal, which is fed to the control amplifier to form the additional control signal.
- a speed signal which is obtained by a conventional speed sensor on the pump.
- This speed sensor detects the passage of the pump pistons or vanes and generates a corresponding signal.
- This signal is fed in the form of a trigger signal to a signal converter, which is based on a stored characteristic or a stored characteristic field converts the trigger signal into an additional signal, which is fed to the control amplifier to form the additional control signal.
- Operating behavior of the pump generate an adjusted control signal.
- an adaptation can be optimized, for example, to the nominal operation or to a desired operating behavior.
- the signal converter is additionally supplied with the actual value of the pump adjustment, since this reduces the influence of the pump adjustment on the operating noise. Since the course of the adjusting force of the adjusting pistons strongly depends on the operating conditions such as eccentricity and pump pressure, it is advantageous if, in addition to the actual value of the pump adjustment, the actual value of the pump pressure generated is also fed to the signal converter as an input signal.
- the additional control signal can be optimized by appropriately incorporating the disturbance variables acting on the hydraulic clamping of the adjusting element and incorporating it in a characteristic diagram.
- FIG. 1 shows in Figure 1 the known principle circuit diagram of an electrohydraulically adjustable control pump in an open circuit with a control of the pump or the control valve by means of its own pressure supply.
- Figure 2 shows a simplified block diagram of the control device according to the invention.
- the adjustable pump 10 is connected to a pressure medium container 12 via a suction line 11 and conveys this pressure medium via a pressure line 13 to a consumer (not shown).
- the adjusting element of the pump for example the lifting ring 14 (see FIG. 2), is acted upon or fixed by two oppositely acting adjusting pistons 15 and 16.
- the adjusting piston 16 with a smaller piston diameter is connected to the pressure line 13 via a control line 17, so that the smaller adjusting piston 16 is constantly acted upon by the delivery pressure.
- the adjusting piston 15 with a larger effective piston diameter is connected to the control valve 20 via a second control line 18. This is designed, for example, as a 4/4 proportional valve and is moved into its respective switching position by an actuating magnet 21 against the action of a spring 22.
- the control valve 20 is also connected via a line 23 to the pressure line 13 and via a line 24 to a return line 25 or the pressure medium container 12.
- the further structure and the mode of operation of the proportional or control valve 20 are not discussed in detail here, since this is known per se and is not essential to the invention.
- control valve 20 The working position of the control valve 20 is tapped via a displacement transducer 27 and as an actual value signal 36 Control amplifier 28 supplied.
- this control amplifier 28 is supplied with the working position of the adjusting member 14 as a further actual value 34 via a displacement sensor 29 arranged on the piston pump 10.
- This control amplifier 28 controls the control valve 20, taking into account the respective input signals.
- Control line 31 driven by control amplifier 28.
- An operating setpoint is specified for this control amplifier by a setpoint input 32.
- the actual value signal 34 of the displacement transducer 29 arranged on the adjusting element 29 is fed to the setpoint specification.
- the corresponding input signal of the control amplifier 28 is supplied with the actual value signal 36 of the pilot valve from the displacement sensor 27.
- a speed sensor 38 is arranged on the pump, which generates a signal when a pump piston or vane (not shown) passes by.
- a trigger signal Up is generated by the speed sensor during operation of the piston pump and is fed to a signal converter 39.
- This trigger signal Ui is converted on the basis of a characteristic field or a characteristic stored in the signal converter 39 into an additional signal U A , which is fed as a further input signal to the output stage of the control amplifier 28.
- Additional signal U ⁇ is modified from the trigger signal O ⁇ on the basis of the characteristic curve or the characteristic map stored in the signal converter, so that a superimposed control signal is triggered in the control amplifier 28. This means that the engine forces act on the Compensating force jumps compensated.
- the additional signal U ⁇ is generated in its course and its phase position so that despite the delays occurring in the control valve 20, a temporal encounter of force jump from the engine and counteraction to the
- the characteristic curve or the characteristic diagram stored in the signal converter 39 are, for example, based on the nominal operation of the pump, ie the trigger signal U ⁇ is matched in the signal converter 39 on the basis of the stored characteristic curve of the normal operating behavior to the oscillations occurring due to engine power.
- the signal converter 39 can be supplied with the actual value signal 34 'of the displacement sensor 29 on the adjusting element.
- the actual value of the pump pressure Pp and / or a signal detected by a sensor 40 on the pump 10 can be given to the converter 39 either individually or in combination with the others
- a servo valve can also be used for the control valve controlling the adjustment piston.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Positive-Displacement Pumps (AREA)
- Reciprocating Pumps (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE4410719A DE4410719A1 (de) | 1994-03-28 | 1994-03-28 | Elektrohydraulisch verstellbare Pumpe |
DE4410719 | 1994-03-28 | ||
PCT/DE1995/000402 WO1995026470A1 (de) | 1994-03-28 | 1995-03-23 | Elektrohydraulisch verstellbare pumpe |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0832360A1 true EP0832360A1 (de) | 1998-04-01 |
EP0832360B1 EP0832360B1 (de) | 1999-09-08 |
Family
ID=6514054
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP95913049A Expired - Lifetime EP0832360B1 (de) | 1994-03-28 | 1995-03-23 | Elektrohydraulisch verstellbare pumpe |
Country Status (6)
Country | Link |
---|---|
US (1) | US5879136A (de) |
EP (1) | EP0832360B1 (de) |
JP (1) | JPH09510764A (de) |
KR (1) | KR100329451B1 (de) |
DE (2) | DE4410719A1 (de) |
WO (1) | WO1995026470A1 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008061828A1 (de) | 2008-12-11 | 2010-06-17 | Robert Bosch Gmbh | Hydrostatische Pumpe, insbesondere Axialkolbenpumpe |
US8429908B2 (en) | 2009-12-17 | 2013-04-30 | Deere & Company | Hydraulic system |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19602729C2 (de) * | 1995-12-06 | 2001-03-01 | Mannesmann Vdo Ag | Verfahren und Anordnung zur Ansteuerung einer elektrohydraulischen Druckversorgung für eine Hilfskrafteinrichtung eines Kraftfahrzeuges |
DE19504220A1 (de) * | 1995-02-09 | 1996-08-14 | Bosch Gmbh Robert | Verstellbare hydrostatische Pumpe |
DE19724870A1 (de) | 1997-06-12 | 1998-12-17 | Bosch Gmbh Robert | Verstellbare hydraulische Arbeitsmaschine |
DE19828752A1 (de) * | 1998-06-27 | 1999-12-30 | Bosch Gmbh Robert | Regelanordnung für ein hydraulisches System |
DE102013201266A1 (de) | 2013-01-28 | 2014-07-31 | Zf Friedrichshafen Ag | Verfahren zur Erhöhung des Wirkungsgrades eines eine verstellbare hydraulische Pumpe aufweisenden Getriebes |
DE102015219990A1 (de) * | 2015-10-15 | 2017-04-20 | Zf Friedrichshafen Ag | Verfahren zum Betreiben einer Pumpenanordnung mit einer Verstellpumpe |
DE102020002868A1 (de) | 2020-05-13 | 2021-11-18 | Hydac Mobilhydraulik Gmbh | Steuerungsverfahren für ein teilelektronisches System |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2111359A1 (de) * | 1971-03-10 | 1972-09-28 | Bosch Gmbh Robert | Regeleinrichtung fuer eine Hydropumpe |
US4285639A (en) * | 1979-06-12 | 1981-08-25 | Parker-Hannifin Corporation | Electronic control for variable displacement pumps |
US4801247A (en) * | 1985-09-02 | 1989-01-31 | Yuken Kogyo Kabushiki Kaisha | Variable displacement piston pump |
US4655689A (en) * | 1985-09-20 | 1987-04-07 | General Signal Corporation | Electronic control system for a variable displacement pump |
EP0367476A1 (de) * | 1988-11-02 | 1990-05-09 | Vickers Systems Limited | Pumpen mit variabler Verdrängung |
JPH02238179A (ja) * | 1988-11-17 | 1990-09-20 | Daikin Ind Ltd | 可変容量形ポンプ |
DE3844059A1 (de) * | 1988-12-28 | 1990-08-30 | Allweiler Ag | Vorrichtung und verfahren zum bewegen von stroemungsmedien |
-
1994
- 1994-03-28 DE DE4410719A patent/DE4410719A1/de not_active Withdrawn
-
1995
- 1995-03-23 US US08/687,511 patent/US5879136A/en not_active Expired - Fee Related
- 1995-03-23 WO PCT/DE1995/000402 patent/WO1995026470A1/de active IP Right Grant
- 1995-03-23 DE DE59506814T patent/DE59506814D1/de not_active Expired - Fee Related
- 1995-03-23 JP JP7524900A patent/JPH09510764A/ja not_active Abandoned
- 1995-03-23 KR KR1019960705295A patent/KR100329451B1/ko not_active IP Right Cessation
- 1995-03-23 EP EP95913049A patent/EP0832360B1/de not_active Expired - Lifetime
Non-Patent Citations (1)
Title |
---|
See references of WO9526470A1 * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008061828A1 (de) | 2008-12-11 | 2010-06-17 | Robert Bosch Gmbh | Hydrostatische Pumpe, insbesondere Axialkolbenpumpe |
US8429908B2 (en) | 2009-12-17 | 2013-04-30 | Deere & Company | Hydraulic system |
Also Published As
Publication number | Publication date |
---|---|
WO1995026470A1 (de) | 1995-10-05 |
JPH09510764A (ja) | 1997-10-28 |
KR100329451B1 (ko) | 2002-09-05 |
DE59506814D1 (de) | 1999-10-14 |
US5879136A (en) | 1999-03-09 |
DE4410719A1 (de) | 1995-10-05 |
KR970701832A (ko) | 1997-04-12 |
EP0832360B1 (de) | 1999-09-08 |
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