EP0826110A1 - Verschiebbare hydraulische leistungs- bzw. momentenregeleinrichtung - Google Patents
Verschiebbare hydraulische leistungs- bzw. momentenregeleinrichtungInfo
- Publication number
- EP0826110A1 EP0826110A1 EP96919743A EP96919743A EP0826110A1 EP 0826110 A1 EP0826110 A1 EP 0826110A1 EP 96919743 A EP96919743 A EP 96919743A EP 96919743 A EP96919743 A EP 96919743A EP 0826110 A1 EP0826110 A1 EP 0826110A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- control
- pressure
- valve
- line
- pump
- 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
- 238000011144 upstream manufacturing Methods 0.000 claims description 2
- 230000001419 dependent effect Effects 0.000 abstract description 5
- 230000001105 regulatory effect Effects 0.000 abstract 3
- 230000000694 effects Effects 0.000 description 2
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
- F04B49/08—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
- F04B2201/1204—Position of a 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
- F04B2205/08—Pressure difference over a throttle
Definitions
- the present invention relates to a power or torque control device for an adjustable hydraulic pump with a hydraulic servo actuator for continuously adjusting the pump delivery rate, in which the delivery rate setting is determined as a function of the delivery pressure of the hydraulic pump in a delivery pressure line and a control pressure in a control line, and the actuator has a spring which sets a pump actuator in the direction of the maximum delivery rate and at least one piston which acts on the pump actuator in the direction of a delivery rate reduction, the piston surface of which can be acted upon by the delivery pressure or connected to a discharge via a hydraulically operated control valve, and the actuation of the control valve by the control pressure in the control line takes place, a torque valve being provided, the closing force of which is determined by a measuring spring arrangement which is connected to the pump actuator and is a function of v is biased on the delivery rate setting, and wherein the torque valve connects the control line depending on the control pressure in the control line and the bias of the measuring spring assembly with the drain.
- Such a control device is known from EP 0 149 787.
- This known control device can be operated either as a torque control or as a power control, depending on whether an optionally adjustable flow restrictor is provided in the delivery pressure line of the hydraulic pump or not.
- torque control the relationship applies that the product of the operating pressure and the stroke volume of the pump must be constant. If the pump speed is constant, torque control is also power control.
- Output controls also detect and control changes in the speed of the pump, which affects the flow rate, for example.
- a measure of the stroke volume of the hydraulic pump is the position of the pump actuator adjusting the pump delivery rate, which is connected to the torque valve via a measuring spring arrangement connected is.
- the shape of the hyperbolic torque or power curve is determined solely by the design of the characteristic of the measuring spring arrangement.
- This known power or torque control device is very much dependent on the amount of work delivered from the operating pressure line on the load side.
- the amount of work delivered changes, the amount of control oil in the control line also changes, so that the pump is adjusted along its performance hyperbole.
- a change in the position of the power hyperbola that is to say a change in the power setting of the pump, is only possible by directly adjusting the pretension of the measuring spring arrangement by means of a handle.
- This manual adjustment is very cumbersome and time-consuming.
- the object of the present invention is therefore to provide a power or torque control device according to the preamble of appended claim 1, with which the torque or power setting of the hydraulic pump changes in a simple manner and to changing working conditions or to different Loads can be adjusted.
- the present invention makes it possible, in particular, to change the control pressure in the control line by appropriately adjusting the adjustable throttle device, even if the amount of work delivered from the operating pressure line is to remain constant.
- the power setting of the adjustable hydraulic pump can thus be quickly and easily adapted to different working conditions.
- the adjustable throttle device preferably consists of the electrically controlled quantity proportional valve, by means of which the control pressure in the control line can be continuously adjusted. This configuration makes it possible in an advantageous manner Change the pump output setting separately, for example by operating a switch in the cab of the excavator.
- the adjustable throttle device is formed from a switching valve and a throttle arranged parallel to it.
- the output and flow control are effective even when the switching valve is closed.
- a further throttle can be arranged in the control line between the adjustable throttle device, that is to say the switching valve and the throttle parallel to it, and the branch to the control valve and the torque valve.
- an adjustable flow restrictor is arranged in the delivery pressure line between the hydraulic pump and the branch of the control line.
- the adjustable throttle device can be connected to a control device via which different operating modes of the hypropump can be set by means of a separate switch.
- This configuration makes it possible to adapt the power setting of the pump to the respective work by operating the separate switch, for example arranged in the cab of an excavator.
- the control device can additionally be connected to a device for measuring the diesel speed, so that the power setting of the pump can also be controlled or adjusted depending on the diesel speed.
- FIG. 1 shows a first exemplary embodiment of the power or torque control device according to the invention, in which the adjustable throttle device is formed by a quantity proportional valve,
- FIG. 2 shows a second embodiment of the power or torque control device according to the invention, in which the adjustable throttle device is formed by a switching valve and a throttle parallel to it, and
- FIG. 3 is a schematic of a further embodiment in which the power setting of the pump by a separate switch and
- Control device can be changed
- FIG. 4 shows a further exemplary embodiment of the present invention, in which two operating pressure lines, each with a corresponding adjustable throttle device, are provided, which optionally act on the power or torque control device according to the invention.
- Figure 1 shows a hydraulic pump 1, which is driven via a shaft 2 by a drive, not shown.
- the hydraulic pump 1 can be, for example, an adjustable axial piston pump which has a pump actuator 3, the pivoting angle of which is proportional to the stroke volume of the hydraulic pump 1.
- a servo actuator for adjusting the swivel angle of the hydraulic pump comprises a spring 4 and a pressurized piston 5, the spring 4 adjusting the hydraulic pump 1 to a maximum swivel angle, that is to say to the maximum delivery volume.
- the piston area of the piston 6 is substantially larger than that of the piston 5.
- the actuating pressure of a signal pressure line 7 acting on the piston 6 or on its piston area is taken from the delivery pressure line 10 of the hydraulic pump 1 via a control valve 8 and the line 9.
- a pressure relief valve 11 is connected in series with the control valve.
- the control valve 8 is designed as a pressure compensator, so it can also be referred to as a pressure valve and is acted upon on the one hand by the delivery pressure of the line 9 and on the other hand by a control pressure of a control line 12.
- the control pressure or the control oil quantity in the control line 12 can be adjusted via an adjustable throttle device 13 which is arranged in the control line 12.
- the control line 12 takes the load-dependent operating pressure of the hydraulic pump 1 from an operating pressure line 15 behind an optionally adjustable flow restrictor 16 from.
- the amount of control oil in the control line can thus be changed in a simple manner by the adjustable throttle device 13.
- the optionally adjustable delivery flow throttle 16 limits the delivery flow of the hydraulic pump 1 in the delivery pressure line 10.
- the delivery pressure and the control pressure acting on the control valve 8 are reduced in front of and behind the delivery flow throttle 16. In this case, it is a power regulation. If the flow throttle 16 is not present, torque control is obtained.
- the torque valve 17 is acted upon on the one hand by the pressure of the control line 12 and on the other hand by a measuring spring arrangement 18, the pretension of which is determined by the position of the piston 6 or the pump actuator 3.
- the torque valve 17 can connect the control line 12 to an unpressurized drain. If the control pressure in the control line 12 reaches the value set on the torque valve 16, it begins to open to the outlet, and a pressure drop occurs at the control slide of the control valve 8.
- the control valve 8 is opened and the piston 6 is actuated via the control pressure line 7 with a control pressure acts and moves this or the pump actuator 3 in the direction of smaller flow rates.
- the measuring spring arrangement 18 of the torque valve 17 is preloaded, so that the pump is adjusted along the power hyperbolas.
- the adjustable one In the first exemplary embodiment shown in FIG. 1, the adjustable one
- Throttle device 13 formed by a quantity-proportional valve 13a, which for
- Example can be electrically controlled. In the closed position of the quantity proportional valve 13a, the power and flow control are switched off.
- FIG. 2 shows a schematic overview of a further exemplary embodiment of the present invention.
- the adjustable throttle device of the power or torque control device 22 of the pump 1 is connected to a control device 20 which can be controlled by means of a separate switch 21.
- Different operating modes that is to say power settings of the pump, can be set by appropriately setting the switch 21.
- the switch 21 shown can be adjusted discretely, but continuous adjustment is also possible. Depending on the work involved, various performance settings of pump 1 can thus be made. It is particularly advantageous that the switch 21 can be arranged separately, for example in the cab of an excavator.
- a device 23 for measuring the speed of the diesel engine 25 driving the pump 1 can be connected to the control device 20. This makes it possible to change the output of the pump 1 continuously or discretely depending on the speed of the diesel engine.
- FIG. 4 shows a further exemplary embodiment of the present invention, in which the components corresponding to the first exemplary embodiment shown in FIG. 1 are identified by the same reference symbols.
- two operating pressure lines 15a, 15b are provided in the exemplary embodiment shown in FIG. 4, which branch off from the delivery pressure line 10.
- Different loads can be operated with the two operating pressure lines 15a, 15b, e.g. a loader block through the operating pressure line 15a and an excavator block through the operating pressure line 15b.
- the number of operating pressure lines that branch off from the delivery pressure line 10 is, however, not limited to two, as in the exemplary embodiment shown in FIG. 4, but the delivery pressure line 10 can branch into any number of operating pressure lines.
- a control line 12a or 12b branches off from each operating pressure line 15a, 15b, in each of which an adjustable throttle device 13a is provided.
- the adjustable throttle devices shown are electrically controlled quantity proportional valves 13a according to the exemplary embodiment shown in FIG. 1, however, the adjustable throttle devices of the exemplary embodiment shown in FIG. 4 can also consist of a switching valve and a throttle arranged in parallel therewith, as in the second exemplary embodiment (FIG. 2 ). If more than two operating pressure lines are provided, a control line branches off from each of these operating pressure lines, in each of which an adjustable throttle device is provided. As shown in Figure 4, the two are Control lines 12a, 12b can be selectively or alternatively connected to the control line 12 via a selection valve 30. The function and effect of the control line 12 has already been described in detail with reference to the first exemplary embodiment shown in FIG. 1.
- a throttle 14 can also be arranged in the control line 12 between the selector valve 30 and the branching of the control line 12 to the control valve 8 and to the torque valve 17 in the exemplary embodiment shown in FIG.
- this throttle 14 is not shown in FIG. 4.
- a possibly adjustable delivery flow throttle 16 can be arranged in the delivery pressure line 10, the control pressure being tapped downstream of this restriction 16 and the delivery pressure upstream of this restriction 16, analogously to the exemplary embodiment shown in FIG. 1.
- This optionally adjustable flow restrictor 16 is also not shown in FIG. 4.
- the adjustable throttle devices 13a, 13a of the exemplary embodiment shown in FIG. 4 can, according to the exemplary embodiment shown in FIG. 3, also be connected to a control device 20 via which different operating modes of the hydraulic pump 1 can be set by means of a separate switch 21. This embodiment is also not shown in FIG. 4.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Fluid-Pressure Circuits (AREA)
- Operation Control Of Excavators (AREA)
- Control Of Positive-Displacement Pumps (AREA)
Abstract
Description
Claims
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19517974 | 1995-05-16 | ||
DE19517974A DE19517974A1 (de) | 1995-05-16 | 1995-05-16 | Verschiebbare hydraulische Leistungs- bzw. Momentenregeleinrichtung |
PCT/EP1996/001970 WO1996036813A1 (de) | 1995-05-16 | 1996-05-09 | Verschiebbare hydraulische leistungs- bzw. momentenregeleinrichtung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0826110A1 true EP0826110A1 (de) | 1998-03-04 |
EP0826110B1 EP0826110B1 (de) | 1999-01-27 |
Family
ID=7762066
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP96919743A Expired - Lifetime EP0826110B1 (de) | 1995-05-16 | 1996-05-09 | Verschiebbare hydraulische leistungs- bzw. momentenregeleinrichtung |
Country Status (5)
Country | Link |
---|---|
US (1) | US5993168A (de) |
EP (1) | EP0826110B1 (de) |
JP (1) | JP4422212B2 (de) |
DE (2) | DE19517974A1 (de) |
WO (1) | WO1996036813A1 (de) |
Families Citing this family (23)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19742157C2 (de) * | 1997-09-24 | 1999-07-01 | Brueninghaus Hydromatik Gmbh | Regeleinrichtung für eine verstellbare Hydropumpe mit mehreren Verbrauchern |
DE19756599C2 (de) * | 1997-12-18 | 1999-12-09 | Brueninghaus Hydromatik Gmbh | Leistungsregelventil und fremddruckgesteuertes Steuerventil |
DE19836917A1 (de) * | 1998-08-13 | 2000-02-17 | Mannesmann Rexroth Ag | Hydraulische Steuereinrichtung zur Druckmittelversorgung eines oder mehrerer hydraulischer Verbraucher, insbesondere einer hydraulischen Formschließeinheit einer Kunststoffspritzgießmaschine |
DE19930618A1 (de) * | 1999-07-02 | 2001-01-04 | Mannesmann Rexroth Ag | Hydraulische Steueranordnung zur Druckmittelversorgung von vorzugsweise mehreren hydraulischen Verbrauchern |
DE19953170B4 (de) * | 1999-11-04 | 2004-08-12 | Brueninghaus Hydromatik Gmbh | Leistungsregelvorrichtung und Ventilblock für eine Leistungsregelvorrichtung |
DE10209964A1 (de) * | 2002-03-06 | 2003-09-25 | Zf Lenksysteme Gmbh | System zur Steuerung einer hydraulischen Verstellpumpe |
US6874318B1 (en) * | 2003-09-18 | 2005-04-05 | Sauer-Danfoss, Inc. | Automatic remote pressure compensation in an open circuit pump |
DE102004061555A1 (de) * | 2004-12-21 | 2006-06-22 | Bosch Rexroth Aktiengesellschaft | Hydraulische Steueranordnung |
DE102005035981A1 (de) * | 2005-07-28 | 2007-02-01 | Putzmeister Ag | Hydraulische Schaltungsanordnung, insbesondere für den Antrieb von Betonverteilermasten |
DE102005051482A1 (de) * | 2005-10-27 | 2007-05-03 | Brueninghaus Hydromatik Gmbh | Lastdruckgeführter Förderstromregler mit Schwingungsdämpfung |
DE102006002959A1 (de) * | 2006-01-21 | 2007-07-26 | Zf Lenksysteme Gmbh | Hydrauliksystem mit volumenstromgeregelter Pumpe |
WO2008022672A1 (de) * | 2006-08-21 | 2008-02-28 | Joma-Hydromechanic Gmbh | Förderpumpe |
DE102006039698B3 (de) * | 2006-08-21 | 2007-10-25 | Joma-Hydromechanic Gmbh | Förderpumpe |
US7726125B2 (en) * | 2007-07-31 | 2010-06-01 | Caterpillar Inc. | Hydraulic circuit for rapid bucket shake out |
GB0912540D0 (en) * | 2009-07-20 | 2009-08-26 | Bamford Excavators Ltd | Hydraulic system |
US8435010B2 (en) * | 2010-04-29 | 2013-05-07 | Eaton Corporation | Control of a fluid pump assembly |
US9086143B2 (en) | 2010-11-23 | 2015-07-21 | Caterpillar Inc. | Hydraulic fan circuit having energy recovery |
CN102536761B (zh) * | 2011-12-26 | 2015-01-07 | 中联重科股份有限公司 | 工程机械及其非电控液压泵的功率控制系统及控制方法 |
DE102013214861A1 (de) * | 2012-08-16 | 2014-05-22 | Robert Bosch Gmbh | Verstellvorrichtung für eine hydrostatische Pumpe und hydrostatische Pumpe |
CN104884818B (zh) * | 2012-12-21 | 2017-06-30 | 伊顿公司 | 流体泵组件的比例流量控制 |
CN110185093A (zh) * | 2019-05-21 | 2019-08-30 | 上海威派格智慧水务股份有限公司 | 一种双罐体结构无负压供水装置 |
CA3115492A1 (en) * | 2020-04-17 | 2021-10-17 | Oshkosh Corporation | Refuse vehicle control systems and methods |
CN114087149B (zh) * | 2021-11-17 | 2023-12-05 | 重庆大学 | 一种双腔独立控制的柱塞泵变量控制回路及多模式切换控制方法 |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
AU6079573A (en) * | 1972-10-11 | 1975-03-27 | Sperry Rand Ltd | Pressure control in hydraulic systems |
DE2906166A1 (de) * | 1979-02-17 | 1980-08-28 | Bosch Gmbh Robert | Einrichtung zur regelung des foerderstroms und zur begrenzung des foerderdrucks einer verstellbaren pumpe |
DE3042837C2 (de) * | 1980-11-13 | 1982-12-09 | Hydromatik Gmbh, 7900 Ulm | Steuer- und Regeleinrichtung bei einem hydrostatischen Getriebe |
US4404009A (en) * | 1982-12-22 | 1983-09-13 | Owens-Corning Fiberglas Corporation | Method and apparatus for forming glass fibers |
DE3345264A1 (de) * | 1983-12-14 | 1985-06-27 | Brueninghaus Hydraulik Gmbh, 7240 Horb | Drehmomenten-regeleinrichtung fuer eine verstellbare hydropumpe |
DE4141108A1 (de) * | 1991-12-13 | 1993-06-17 | Putzmeister Maschf | Einrichtung zur regelung des ausgangsdruckes einer verstellpumpe |
DE4235707B4 (de) * | 1992-10-22 | 2007-10-18 | Linde Material Handling Gmbh | Hydrostatisches Antriebssystem |
DE9217829U1 (de) * | 1992-12-30 | 1993-04-08 | Noell Service Und Maschinentechnik Gmbh, 30853 Langenhagen | Überwachungseinrichtung für eine hydraulisch angetriebene Maschine |
-
1995
- 1995-05-16 DE DE19517974A patent/DE19517974A1/de not_active Ceased
-
1996
- 1996-05-09 DE DE59601232T patent/DE59601232D1/de not_active Expired - Lifetime
- 1996-05-09 EP EP96919743A patent/EP0826110B1/de not_active Expired - Lifetime
- 1996-05-09 WO PCT/EP1996/001970 patent/WO1996036813A1/de active IP Right Grant
- 1996-05-09 US US08/894,078 patent/US5993168A/en not_active Expired - Lifetime
- 1996-05-09 JP JP53452796A patent/JP4422212B2/ja not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO9636813A1 * |
Also Published As
Publication number | Publication date |
---|---|
US5993168A (en) | 1999-11-30 |
DE19517974A1 (de) | 1996-11-21 |
EP0826110B1 (de) | 1999-01-27 |
JPH11505308A (ja) | 1999-05-18 |
JP4422212B2 (ja) | 2010-02-24 |
DE59601232D1 (de) | 1999-03-11 |
WO1996036813A1 (de) | 1996-11-21 |
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