EP1445488A2 - Entraínement avec machine hydraulique - Google Patents

Entraínement avec machine hydraulique Download PDF

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Publication number
EP1445488A2
EP1445488A2 EP04002364A EP04002364A EP1445488A2 EP 1445488 A2 EP1445488 A2 EP 1445488A2 EP 04002364 A EP04002364 A EP 04002364A EP 04002364 A EP04002364 A EP 04002364A EP 1445488 A2 EP1445488 A2 EP 1445488A2
Authority
EP
European Patent Office
Prior art keywords
control
control valve
valve
pressure
inlet side
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.)
Withdrawn
Application number
EP04002364A
Other languages
German (de)
English (en)
Other versions
EP1445488A3 (fr
Inventor
Johann Ballert
Andrè Droux
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.)
Liebherr Machines Bulle SA
Original Assignee
Liebherr Machines Bulle SA
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 Liebherr Machines Bulle SA filed Critical Liebherr Machines Bulle SA
Publication of EP1445488A2 publication Critical patent/EP1445488A2/fr
Publication of EP1445488A3 publication Critical patent/EP1445488A3/fr
Withdrawn legal-status Critical Current

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    • 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

Definitions

  • the present invention relates to a drive with a swallowing volume changeable hydraulic machine, with an adjusting device for changing the Swallowing volume of the hydraulic machine, with a first control valve, the outlet side communicates with the actuating device and is connected in such a way that it in a first position a low swallowing position of the Actuating device and in a second position a large Position of the actuating device that causes the swallowing volume.
  • FIG. 1 shows a hydraulic circuit diagram of a known drive with a in the absorption volume changeable hydraulic motor 11.
  • the adjustment of the swallowing volume of the Hydraulic motor 11 takes place by means of the actuating device 10, the piston chamber shown on the left is connected to the connection 510 of a control valve 5.
  • the Control valve 5 has a control connection 52, which is connected via shuttle valve 6 is pressurized.
  • the shuttle valve 6 is connected to the inlet and outlet line the drive or with the corresponding working connections A, B in Connection.
  • the control valve 5 has a further control connection 54, which via a Control port X can be controlled.
  • control valve 5 On its inlet side 500, the control valve 5 is connected to the line 14, which extends between the working lines 12, 13 of the hydraulic motor 11 and is designed with the check valves 9a and 9b. These ensure that on the inlet side 500 of the control valve 5 the higher one in the working lines 12, 13 pressure is present.
  • the piston space shown on the right is also shown Actuating device 10 with the inlet side 500 of the control valve 5 and thus also with the aforementioned check valve arrangement 9a, 9b or the line 14 in connection.
  • lines 15, 16 connecting work lines 12, 13 are provided, in which preset pressure relief valves 2a, 2b are arranged.
  • the arrangement further comprises the brake valve 1, which the return of the Hydromotor 11 connects either to connection A or B depending on the position or that is in the locked position shown in FIG. 1.
  • the brake valve 1 is controlled via the throttle check valves 8a, 8b.
  • the pump-side high pressure signal is sent via the shuttle valve 6 placed on the control valve 5 or its control connection 52.
  • the control valve moves from the position shown in FIG. 1 in direction 2 moves, so that the inlet 500 with the piston space shown on the left Actuator 10 is connected.
  • the same pressure is according to the chosen one Arrangement also in the piston chamber 10 shown on the right. by virtue of The piston of the actuating device becomes the larger piston area of the left piston chamber 10 moved to the right according to FIG. 1, which has the consequence that the Swallowing volume of the hydraulic motor increased accordingly.
  • the pressure at port A causes the throttle check valve 8a the movement of the brake valve according to FIG. 1 to the right, which results has that the working line 13 of the hydraulic motor 11 via the brake valve 1 with the Connection B is connected, so that a corresponding drain of the hydraulic medium can take place.
  • the hydraulic motor 11 is supplied in accordance with the mentioned embodiment via port A.
  • the pressure here lies on the inlet side of the hydraulic motor 11 and also on the check valve 9a. The pressure is the same depending on the valve arrangement selected the inlet side 500 of the control valve 5 and in the piston chamber shown on the right the actuating device 10.
  • the control valve 5 moves in the direction 1 until the one shown in FIG. 1 Position is reached.
  • the piston chamber shown on the left is the Actuator 10 is relieved and the piston is shifted accordingly to the left.
  • the hydraulic motor 11 operates with a low absorption volume becomes.
  • the braking torque generated in this mode of operation corresponds to that described above Functioning with low swallowing volume (position of the control valve as shown in Fig. 1) of the hydraulic machine and at a relatively high Pressure difference ⁇ p generated. Because of the relatively low swallowing volume a relatively large pressure difference .DELTA.p is required to achieve a predetermined one To generate braking torque.
  • FIG. 2 An exemplary embodiment in FIG. 2 is based on the fact that a control device, preferably in the form a second control valve is provided, which has an inlet pressure on the inlet side is acted upon and on the outlet side with a first control connection of the is connected to the first control valve, a pressurization of the first control connection a directed in the second position of the first control valve Exerts force, and wherein the control device preferably the second Control valve is connected such that it is in a low power range the inlet side with the first control connection of the first control valve combines.
  • a control device preferably in the form a second control valve is provided, which has an inlet pressure on the inlet side is acted upon and on the outlet side with a first control connection of the is connected to the first control valve, a pressurization of the first control connection a directed in the second position of the first control valve Exerts force, and wherein the control device preferably the second Control valve is connected such that it is in a low power range the inlet side with the
  • the first control valve in its second Position is movable, which means that the swallowing volume of the hydraulic machine and thus the braking torque is increased. Accordingly, at constant braking torque a lower pressure difference is required.
  • the control device or the second control valve performs the function of a corresponding one Control connection of the first control valve is at least lower in the range Power demand is pressurized, causing the aforementioned Change in position of the first control valve and thus also the position of the actuating device is changeable in the desired manner. In a preferred embodiment the mentioned area of lower power is reached during the descent.
  • the hydraulic machine can be designed as a hydraulic motor. This can be used as an axial piston motor be designed in a swashplate construction. However, are also conceivable any other embodiment of the hydraulic machine.
  • the first Control valve a second, with its first control connection acting the same Control connection on that with a first control connection of the second control valve communicates so that both control ports have the same control pressure be charged.
  • an inlet and an outlet line of the drive extends a line having a shuttle valve, by means of which the control pressure to the second control port of the first control valve and on the first control connection of the second control valve can be applied.
  • the second control valve a second control connection counteracting the first control connection and that the second control connection with the inlet side of the communicates with the first control valve, so that on the inlet side of the first Control valve and the same at the second control port of the second control valve Pressure is present.
  • a pressure reducing valve provided that the outlet side with the inlet side of the second control valve in Connection is established.
  • the outlet pressure of the pressure reducing valve is accordingly via the second control valve to the first control connection of the first Control valve created.
  • the pressure reducing valve on the inlet side with the Inlet side of the first control valve communicates.
  • the second control valve with the control connection of one or more pressure relief valves in Connection is established, the pressure relief valves in the working lines of the Hydraulic machine connecting lines are added, and being the second Control valve is connected in such a way that its inlet side with the control connections the pressure relief valve can be connected.
  • This way can be achieved be that the pressure level of the pressure relief valves is changeable and be increased accordingly, for example, when the required torque is high can.
  • the braking torque is thus not only by adjusting the first control valve and thus by the Changes in the swallowing volume, but also through targeted control the pressure relief valves changeable.
  • the second control valve is connected in such a way that that it is in its inlet side with the first control port of the first control valve connecting position the control connections of the pressure relief valves switches without pressure and in the inlet side with the control connections of the pressure relief valves connecting position the first control connection of the first Control valve switches depressurized.
  • a brake valve is provided which is in a closed position with a low power requirement and in this position blocks the return of the hydraulic machine.
  • pressure lines can be provided, by means of which the first Control valve and / or the second control valve and / or the pressure reducing valve can be overridden are.
  • Fig. 2 shows the circuit diagram of the drive according to the invention in its Swallowing volume adjustable hydraulic motor 11 and the associated control.
  • the inventive one has Drive according to the embodiment of FIG. 2, a pressure reducing valve 4 and a second control valve 3.
  • pressure relief valves 2 provided, which are adjustable via corresponding control connections 20.
  • connection 310 of the second control valve 3 is also present the first control port 50 of the first control valve 5.
  • the pump-side high pressure signal is sent via the shuttle valve 6 to the second control valve 3 (control connection 30), which is designed as a directional valve and the first control valve 5 (control connection 52).
  • the second control valve 3 control connection 30
  • the second control port 52 of the first control valve 5 control connection 52
  • the pressure reducing valve 4 on its inlet side 410, the second control port 32 of the second control valve 3 and the inlet side 500 of the first control valve 5 is supplied with pressure.
  • This pressure is beyond on the piston chamber of the actuating device 10 shown on the right. by virtue of the connection of the inlet side 410 of the pressure reducing valve 4 to the shuttle valve 9 ensures that the pressure reducing valve 4 both during acceleration is fed with high pressure when braking.
  • the first control valve 5 moves accordingly large pressure applied to the second control port 52 in the direction 2, i. H. in its left end position, in which the inlet side 500 with the connection 510 and thus in connection with the piston chamber of the actuating device 10 shown on the left stands. Due to the larger piston area in the piston chamber shown on the left the actuating device 10 moves to the right and thus the swallowing volume of the Hydraulic motor 11 enlarged.
  • the one at start-up on the shuttle valve 6 and thus also on the first control connection 30 of the second control valve 3 applied control pressure also causes that the second control valve 3 also in direction 2 and thus in its left End position is moved. This movement is based on the corresponding Preload the valve.
  • the on the first control connection 30 and on the second control port 32 of the second control valve 3 applied control pressures are identical in this mode of operation.
  • the hydraulic motor In this operating state, the hydraulic motor is at maximum absorption volume set and the control pressure of the pressure reducing valve 4 brings about the second Control valve 3 the high pressure valves 2 to their maximum setting. This will ensures that the hydraulic motor 11 delivers the maximum torque.
  • the first control valve 5 moves due to the dropping control pressure at the second control connection 52 in direction 1, whereby the swivel angle and the swallowing volume of the hydraulic motor become smaller and the speed increases (high speed / low torque).
  • the reverse drive can be achieved by swapping connections A and B. This works in the same way as described above.
  • the hydraulic motor 11 now works as a hydraulic pump that holds the hydraulic medium promotes in the circuit via the pressure relief valves 2.
  • the increase in the return pressure at the shuttle valve 9 and the simultaneous decrease of the inlet pressure at the shuttle valve 6 has the consequence that the second control valve 3 in direction 1 and the first control valve 5 is moved in direction 2.
  • this connects the outlet side 400 of the pressure reducing valve 4 via the connection 310 to the first control connection 50 of the first control valve 5, which has the consequence that this in direction 2 is moved and accordingly the swivel angle of the hydraulic motor 11 goes to its maximum value or the swallowing volume to the maximum value is set.
  • the second control valve 3 relieves the control connections 20 of the pressure relief valves 2, so that the pressure setting accordingly is reduced.
  • the braking torque remains due to the correspondingly increased Swallowing volume constant. With this setting, the noise level is reduced.
  • Embodiment also conceivable without pressure reducing valve 4. In this case it takes place the subsequent valves are controlled directly with the system high pressure. This means that in this case the second control valve 3 and the pressure relief valves 2 and the first control valve 5 designed and suitable for high pressure must be carried out.
  • the response of the control valve 5 is delayed takes place so that braking begins with a minimum swallowing volume, so on At the beginning of the braking process the engine does not overturn.
  • the delay can be over the control valve 5 can be adjustable.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
EP04002364A 2003-02-05 2004-02-03 Entraínement avec machine hydraulique Withdrawn EP1445488A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10304665A DE10304665A1 (de) 2003-02-05 2003-02-05 Antrieb mit Hydromaschine
DE10304665 2003-02-05

Publications (2)

Publication Number Publication Date
EP1445488A2 true EP1445488A2 (fr) 2004-08-11
EP1445488A3 EP1445488A3 (fr) 2004-09-01

Family

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Family Applications (1)

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EP04002364A Withdrawn EP1445488A3 (fr) 2003-02-05 2004-02-03 Entraínement avec machine hydraulique

Country Status (3)

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US (1) US20040244369A1 (fr)
EP (1) EP1445488A3 (fr)
DE (1) DE10304665A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN101922445B (zh) * 2010-07-29 2013-08-21 杭州力龙液压有限公司 一种恒功率控制阀

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4399886A (en) * 1980-12-09 1983-08-23 Sundstrand Corporation Controls for variable displacement motor and motors
US4498847A (en) * 1982-06-29 1985-02-12 Kabushiki Kaisha Komatsu Seisakusho Control system for variable displacement hydraulic pumps
JPH0745652Y2 (ja) * 1990-03-09 1995-10-18 新キャタピラー三菱株式会社 走行速度切換装置
DE4029548A1 (de) * 1990-09-18 1992-03-19 Hydromatik Gmbh Steuer- und regelvorrichtung fuer ein hydrostatisches getriebe
DE4329689C1 (de) * 1993-09-02 1995-02-23 Hydromatik Gmbh Steuervorrichtung für ein hydrostatisches Getriebe
DE19831587C2 (de) * 1998-07-14 2000-06-15 Brueninghaus Hydromatik Gmbh Leistungsregelvorrichtung zur Regelung der hydraulischen Leistung einer Hydropumpe
DE19953170B4 (de) * 1999-11-04 2004-08-12 Brueninghaus Hydromatik Gmbh Leistungsregelvorrichtung und Ventilblock für eine Leistungsregelvorrichtung
DE10037195A1 (de) * 2000-07-31 2002-02-14 Linde Ag Hydrostatische Maschine

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Publication number Publication date
DE10304665A1 (de) 2004-08-19
US20040244369A1 (en) 2004-12-09
EP1445488A3 (fr) 2004-09-01

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