EP2179176B1 - Système hydraulique avec une machine hydrostatique réglable - Google Patents

Système hydraulique avec une machine hydrostatique réglable Download PDF

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Publication number
EP2179176B1
EP2179176B1 EP08801632A EP08801632A EP2179176B1 EP 2179176 B1 EP2179176 B1 EP 2179176B1 EP 08801632 A EP08801632 A EP 08801632A EP 08801632 A EP08801632 A EP 08801632A EP 2179176 B1 EP2179176 B1 EP 2179176B1
Authority
EP
European Patent Office
Prior art keywords
piston
actuating
valve
force
control
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.)
Not-in-force
Application number
EP08801632A
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German (de)
English (en)
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EP2179176A1 (fr
Inventor
Clemens Krebs
Timo Nafz
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.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP2179176A1 publication Critical patent/EP2179176A1/fr
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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
    • F04B1/30—Control of machines or pumps with rotary cylinder blocks
    • F04B1/32—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block
    • F04B1/324—Control of machines or pumps with rotary cylinder blocks by varying the relative positions of a swash plate and a cylinder block by changing the inclination of the swash 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
    • 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
    • F04B1/20—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 having rotary cylinder block
    • F04B1/2014—Details or component parts
    • 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
    • F04B2201/00—Pump parameters
    • F04B2201/12—Parameters of driving or driven means
    • F04B2201/1204—Position of a rotating inclined plate
    • F04B2201/12041—Angular position
    • 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
    • F04B2201/12051—Angular position

Definitions

  • the invention relates to a hydraulic system with an adjustable hydrostatic machine, a co-operating with the hydrostatic machine actuator and a control valve, wherein the actuating device has at least a first actuating piston, which is acted upon on a control piston surface with a control pressure, and wherein the control valve has a control element, which is acted upon in the direction of a first end position of the valve with a dependent on the position of the first actuating piston force and which is acted upon for adjusting a control valve position at a second end with a force.
  • a hydrostatic system with an arranged in an open circuit variable displacement hydraulic pump according to the preamble of claim 1 is known.
  • the adjusting mechanism of the hydraulic pump is actuated by an adjusting device.
  • the adjusting device has an actuating piston which defines a control pressure chamber formed in a control cylinder.
  • the control pressure prevailing in the signal pressure chamber is regulated by a control valve.
  • the control pressure chamber is variably connectable with a delivery-side working line of the hydraulic pump or a tank volume for setting a control pressure acting on the control piston surface of the control piston via the control valve.
  • the control valve has a valve piston as a valve piston which is acted upon at a first end with the force of a feedback spring.
  • the feedback spring supported on the one hand at one end of the valve piston and on the other hand on the acted upon by the control pressure piston surface of the actuating piston.
  • the force generated by the feedback spring on the valve piston is thus dependent on the position of the actuating piston.
  • the force of an electromagnet acts on the valve piston, the force of an electromagnet.
  • a proportional adjustment of the actuating piston is thus achieved as a function of a control signal of the proportional magnet.
  • the EP 0 849 468 A2 shows an adjusting device for adjusting the delivery volume of an axial piston pump.
  • the adjusting device comprises an actuating piston adjoining the delivery volume of the axial piston pump in a force-locking manner.
  • a control valve is provided, which has a valve piston on which a connecting member bears non-positively.
  • On the connecting member engages a return spring, which is supported on a first spring plate.
  • a feedback spring is arranged, which acts on a voltage applied to the connecting member second spring plate.
  • a Ausschwenkfeder is provided, which is clamped between the first spring plate and a substantially formed as a hollow cylinder stop element.
  • the EP 0 859 380 A2 shows an electromagnetic Doppelhubmagneten.
  • the WO 03/014570 A1 shows a valve block for a control device, in particular for a hydrostatic machine, with a pressure control valve and a flow control valve, each having a valve piston and a return spring.
  • the hydraulic system according to the invention has an adjustable hydrostatic machine, an adjusting device interacting with an adjusting mechanism of the hydrostatic machine and a control valve.
  • the adjusting device has at least one actuating piston, which is acted on at least on an actuating piston surface with a control pressure.
  • the control valve has as a control element to a valve piston which is acted upon by a dependent of the position of the actuating piston force. To set the desired position of the adjusting mechanism, the control element can be acted upon by a control force which can be generated by actuating means.
  • the hydrostatic system according to the invention therefore has the advantage that not only an adjustment of a hydraulic pump between, for example, a zero delivery volume and its maximum delivery volume is possible, but that also in opposite directions pivotable hydrostatic machines, such as provided for two flow directions pumps or a pump / Motor unit, as used in braking energy recovery devices can be controlled in a simple manner.
  • the counterforce is preferably generated by a spring and the control force is preferably continuously adjustable in both directions of force.
  • the actuating means preferably comprises two, acting in opposite directions on the valve piston proportional solenoids.
  • Such proportional magnets are simple and inexpensive available.
  • control valve in a hydrostatic machine is possible by controlling both actuating directions by only one actuator as actuating means, in which the acted upon by the position-dependent force side of the control element is not accessible.
  • the actuating means is preferably designed according to an alternative embodiment as Doppelhubmagnet with a first winding and a second winding.
  • a force is generated by each of the windings in each case one of the opposite directions of force.
  • the direction of force and also the magnitude of the force can be predetermined in a simple manner by two individual control signals.
  • the use of only one actuator for both directions of force also has the advantage that the line and plug expenses can be kept small.
  • a particularly simple construction is achieved if the feedback spring is arranged between the actuating piston and the valve piston.
  • the hydrostatic machine is set with vanishing control force and an equilibrium of forces between the opposing force and the dependent of the position of the actuating piston force on the control element to a non-zero delivery volume.
  • the adjusting device preferably has, in addition to the actuating piston, which acts on the hydrostatic machine from a rest position in the direction of a first end position with a restoring force, another, also referred to opposing piston piston, the hydrostatic machine in the opposite direction, starting from the rest position in the direction a second end position acted upon by a force.
  • actuating piston which acts on the hydrostatic machine from a rest position in the direction of a first end position with a restoring force
  • another, also referred to opposing piston piston the hydrostatic machine in the opposite direction, starting from the rest position in the direction a second end position acted upon by a force.
  • the limited by the piston surface of the actuating piston control pressure chamber is preferably connected via the control valve with a control pressure source.
  • the control pressure source is connected in particular via a connecting line in which a pressure reducing valve is arranged with the control valve.
  • the connecting line with the pressure reducing valve provided therein has the advantage that by means of the pressure reducing valve, a reduced compared to the working pressure input pressure is generated.
  • This can be used as a control pressure source, for example, depending on different operating situations of the hydrostatic system pressure.
  • the delivery pressure of the hydrostatic machine may be provided as a control pressure source.
  • the second actuating piston has a smaller compared to the first actuating piston piston surface, the immediate is acted upon by the working pressure of the hydrostatic machine.
  • the control pressure source is preferably a working line of the hydrostatic machine or a further pressure medium source.
  • the working line or the pressure medium source are connected via a shuttle valve to the connecting line.
  • the possibility of alternatively providing a further pressure medium source in addition to the working line as an actuating pressure source has the advantage that even when the working line pressure disappears, a control pressure sufficient for actuating the hydrostatic system is available. This is particularly advantageous when the hydrostatic system is used in the recovery of kinetic energy by storing the energy in a hydrostatic accumulator. During operation, it may happen that the hydrostatic accumulator is completely emptied. In this case, a sufficient actuating pressure in the first control pressure chamber can be generated by the further pressure medium source, through which the hydrostatic machine can be set to a higher delivery volume in a subsequent storage of energy.
  • the control valve is preferably designed as a 3/3-way valve.
  • the use of a 3/3-way valve makes it possible to additionally provide a neutral position of the control valve between the two end positions. This neutral position is determined by a defined control valve position.
  • the actuating pressure chamber which is limited by the actuating piston surface of the first actuating piston, is preferably throttled with a tank volume and throttled to the control pressure source.
  • control pressure chamber In the first end position of the control valve, the control pressure chamber is connected to the control pressure source. In the opposite second end position of the control valve, however, the limited by the control piston surface of the first control piston actuating pressure chamber is connected to a tank volume.
  • the 3/3-way valve is variably adjustable between these two end positions.
  • the hydrostatic system 1 has, according to a first embodiment, a hydrostatic machine 2.
  • the hydrostatic machine 2 is designed as a pump / motor machine.
  • the hydrostatic machine 2 is designed to be adjustable in terms of its stroke volume and preferably a hydrostatic axial piston machine in swash plate construction, which is pivotable from a neutral position in two directions. The stroke volume is adjusted by adjusting the swash plate.
  • the hydrostatic machine 2 is connected to a first working line 3 and a second working line 4.
  • the first working line 3 connects the hydrostatic machine 2 with a hydraulic accumulator 6.
  • the second working line 4 is connected to a tank volume 7.
  • the hydrostatic machine 2 can be operated as a pump, so that it via the second working line. 4 Pressure medium from the tank volume 7 sucks and promotes via the first working line 3 against the pressure prevailing in the hydraulic accumulator 6 pressure. This pressure energy can be stored in the hydraulic accumulator 6.
  • a drive shaft 5 is provided, which connects the hydrostatic machine 2 with a drive train of a vehicle. By adjusting the delivery volume of the operated as a pump hydrostatic machine 2 with simultaneous connection of the drive shaft 5 to the drive train of a vehicle pressure medium is promoted in a hydraulic brake of the vehicle in the hydraulic accumulator 6 and thus braked the vehicle.
  • the adjusting device comprises a first actuating piston 8 and a second actuating piston 9.
  • the first actuating piston 8 is displaceably arranged in a first actuating cylinder 10 and is connected to the adjusting mechanism of the hydrostatic machine 2 mechanically coupled.
  • the first control piston 8 thrust forces on, for example, the swash plate as adjustment of the hydrostatic machine 2 can be transmitted.
  • the second actuating piston 9 is arranged displaceably in a second actuating cylinder 11. Also, the second actuating piston 9 can transmit shear forces on the adjusting mechanism of the hydrostatic machine 2, but with opposite effect with respect to the pivoting direction.
  • the adjusting pistons 8 and 9 engage opposite sides of the swashplate of the hydrostatic machine 2, so that a further adjustment of the hydrostatic machine 2 is avoided in the case of an equilibrium of forces between the two forces transmitted to the swashplate by the adjusting pistons 8 and 9.
  • a first control pressure chamber 12 and in the second control cylinder 11 are formed in the first actuating cylinder 10.
  • the two control pressure chambers 12, 13 are limited by the first control piston 8 or the second control piston 9 on one side.
  • a hydraulic force is thus generated at a first control piston surface 14 of the first control piston 8 delimiting the first control pressure chamber 12.
  • This hydraulic force is transmitted to the adjusting mechanism of the hydrostatic machine 2 via a corresponding linkage.
  • the pressure prevailing in the second actuating pressure chamber 13 on the second actuating piston surface 15 of the second actuating piston 9 in the opposite direction to the Adjusting mechanism of the hydrostatic machine 2 generates acting force.
  • a control valve 16 In order to set the control pressure prevailing in the first control pressure chamber 12, a control valve 16 is provided. A first connection of the control valve 16 is connected via a control pressure line 17 to the first control pressure chamber 12. Depending on the position of a control element of the control valve 16, the control pressure line 17 is connected to a control pressure source or the tank volume 7. For this purpose, a second connection of the control valve 16 is connected via a connecting line 18 with a shuttle valve 19. With the aid of the shuttle valve 19, either the first working line 3 or else a further pressure medium source is connected via the further connecting line 20 to the connecting line 18 as a control pressure source. Via the further connecting line 20 can be fed from an external pressure medium source pressure medium. This can be useful, for example, if the residual pressure available in the hydraulic accumulator 6 is not sufficient to actuate the adjusting device.
  • a pressure reducing valve 21 is provided in the connecting line 18.
  • the pressure reducing valve 21 has a measuring surface which is acted upon by the output pressure of the pressure reducing valve 21, which is supplied to the control valve 16.
  • the force of a spring over which the start of control of the pressure reducing valve 21 is set.
  • the control valve 16 is thus supplied with a constant input pressure, if on the input side of Pressure Reducing Valve 21 a sufficient pressure is available through the control pressure source.
  • the control valve 16 has a control valve element, which is preferably designed as a valve piston.
  • This valve piston is arranged axially displaceably in a valve housing and has a first end and a second end remote from it. The first end of the valve piston is acted upon by the control pressure prevailing in the first control pressure chamber 12 and limits the first control pressure chamber 12.
  • a feedback spring 22 is arranged between the first control piston 8 and the valve piston of the control valve 16.
  • a force acts on the valve piston of the control valve 16, which force is generated by the feedback spring 22 and depends on the position of the first actuating piston 8.
  • a counterforce which is generated by a spring 23 In the opposite direction acts on the valve piston, a counterforce which is generated by a spring 23.
  • the spring 23 is designed to be adjustable, so that the position of the first actuating piston 8, in which the valve piston is in an equilibrium of forces between the feedback spring 22 and the spring 23, can be adjusted. The preferred setting will be described below with reference to FIGS Fig. 2 still explained.
  • the control valve 16 is designed pressure-compensated. For this purpose branches of the control pressure line 17 from a line branch, which acts on the valve piston at its second end in the same direction with the spring 23 with a hydraulic force. The force acting in the control pressure chamber 12 on the first end of the valve piston hydraulic force is thus by a correspondingly large hydraulic force compensated for the second end. For an integrated arrangement of the control valve 16 in the actuator is possible. The pressure reduction is integrated in the actuator.
  • control valve 16 In the Fig. 1 the control valve 16 is shown in its neutral position. In this neutral position, the first connection of the control valve 16 is connected in a throttled manner to the second connection of the control valve 16 and to a third connection of the control valve 16. The third port is connected to the tank volume 7.
  • the control valve 16 is designed with negative overlap.
  • the control valve 16 is adjustable in the direction of a first end position and in the direction of a second end position.
  • the control valve 16 can assume any intermediate position between the two end positions.
  • the first port is connected to the second port of the control valve 16 unthrottled or almost unthrottled.
  • a connection between the connecting line 18 and the actuating pressure line 17 is generated.
  • the first port and thus the control pressure line 17 is connected to the tank volume 7 via the third port of the control valve 16 unthrottled or almost unthrottled.
  • the first control pressure chamber 12 is connected in the second end position of the control valve 16 to the tank volume 7 and the pressure in the first control pressure chamber 12 is expanded into the tank volume 7.
  • the connecting line 18 is also connected in a section between the shuttle valve 19 and the pressure reducing valve 21 to the second control pressure chamber 13.
  • the hydrostatic machine 2 is adjusted until an equilibrium of forces prevails.
  • the actuating piston surface 15 of the second actuating piston 9 is smaller than the actuating piston surface 14 of the first actuating piston eighth
  • an actuator 24 is provided at the second end of the valve piston of the control valve 16.
  • This actuator 24 is designed as Doppelhubmagnet with two windings.
  • a first control signal By applying a first control signal to this first winding, a pressure force can be generated as a control force at the second end of the valve piston.
  • a control force in a first force direction which acts in the same direction with the counterforce of the spring 23 on the valve piston, is generated.
  • a force against the force of the spring 23 can be generated. The resultant of the force of the spring 23 and the force of the actuator 24 acts on the second end of the valve piston.
  • the movement of the first actuating piston 8 takes place in each case until, again, a balance of forces between the resultant and the force of the feedback spring 22 has set and the control valve again in the in Fig. 1 shown rest position is.
  • the position of the first actuating piston 8 and thus the set stroke volume of the hydrostatic machine 2 is in each case proportional to the control signals supplied to the actuator 24 for a respective direction of movement.
  • the maximum possible pivot angle of the hydrostatic machine 2 is adjusted by mechanical stops which are formed on the adjusting mechanism of the hydrostatic machine 2.
  • a first return spring 25 and a second return spring 26 are provided.
  • a pair of driving elements 27, 27 ' is provided.
  • the first return spring 25 is supported on a displaceably arranged spring plate 28. This is displaceable on the linkage and is based on a movement to the right of the housing side. In an adjusting movement, in which the first actuating piston 8 in the Fig. 1 is adjusted to the right, so that the first return spring 25 is compressed beyond its bias.
  • the second return spring 26 is supported via a displaceably arranged further spring plate 29 at an opposite adjustment on the housing side.
  • the second return spring 26 is biased between a pair of further driving elements 30 30 '.
  • either the first restoring spring 25 or the second restoring spring 26 is compressed in this case outside of a small adjustment range about the rest position.
  • the respective other return spring 25 and 26 is moved simultaneously with the linkage.
  • the driving elements 27, 27 'and 30, 30' are arranged on the linkage, that the return springs 25 and 26 are biased and abut the displaceable spring plates 28, 29.
  • the displaceable spring plates 28, 29 are arranged, even if this is not absolutely necessary, in a rest position of the hydrostatic machine 2 at a distance from the housing. In principle, it is also possible without a gap to the housing. Due to the distance component tolerances can be easily compensated.
  • the bias of the return springs 25, 26 between the driving elements 27, 27 'and 30, 30' the assembly is considerably simplified, since a pre-assembly can take place.
  • the adjustment of the hydrostatic machine 2 is explained again with reference to a diagram.
  • the currents I 1 of a first control signal and a second control signal I 2 for energizing the first winding and the second winding are shown.
  • the delivery volume V P during operation of the hydrostatic machine 2 as a pump or the displacement V M during operation of the hydrostatic machine 2 are shown as a motor. It can be seen that the hydrostatic machine 2 from an electroless neutral position out in Both directions can be adjusted up to the 100% end position.
  • the spring 23 of the control valve 16 is adjusted so that the neutral position of the control valve 16 is achieved in a position of the first control piston 8, which corresponds to a deflection of the hydrostatic machine 2 from its rest position to a minimum displacement V P, min .
  • Such a setting of the hydrostatic machine 2 with vanishing control signal for the actuator 24 ensures that when the drive shaft 5 is connected to the drive train of a vehicle by the hydrostatic machine 2, a minimum pressure in the first working line 3 by conveying pressure medium into the hydraulic accumulator. 6 is built. This ensures that by the hydraulic system 1 at any time sufficient to actuate the actuator pressure is available and the hydrostatic machine has no intake problems due to wrong pivot side.
  • the design of the area ratios of the first actuating piston 8 to the surface of the second actuating piston 9 is preferably about 3/1.
  • the pressure reducing valve 21 is preferably set to reduce to about 2/3 of the working pressure.
  • the working pressure is the maximum storage pressure of the hydraulic accumulator 6.
  • a pressure of about 1/3 of the working pressure is required to achieve a force equilibrium between the two adjusting pistons 8,9.
  • Fig. 3 shows a modified embodiment.
  • the function is essentially the same as with reference to Fig. 1 explained function, which is why below only the changes compared to the first embodiment will be discussed.
  • the control valve 16 ' is not arranged here in the axial extension of the first actuating cylinder 10.
  • the free arrangement of the control valve 16 ' allows, as actuating means in place of the Doppelhubmagneten 24, as shown in the Fig. 1 is used to provide a first proportional magnet 24.1 and a second proportional magnet 24.2.
  • the two proportional solenoids 24.1. and 24.2 are each adapted to transmit thrust forces to the valve piston of the control valve 16 '.
  • the position of the adjusting mechanism can also be tapped via the connection between the second actuating piston 9 and the adjusting mechanism of the hydraulic machine 2 done. This is done in the illustrated embodiment via a linkage 31st
  • the feedback spring 22 ' is supported, which acts on the valve piston at one end with the force dependent on the position of the adjusting mechanism. In the opposite direction acts, as already with reference to the Fig. 1 has been explained, a counter force, which is generated by a spring 23 '.
  • vanishing control force ie, without applied control signal to the first proportional solenoid 24.1 and the second proportional solenoid 24.2
  • the force of the feedback spring 22 'and the opposing force of the spring 23' are in an equilibrium of forces when the hydraulic Machine 2 is in its rest position.
  • the hydraulic system also sets itself here so that the resultant of the control force, which is now generated by the two proportional magnets 24.1 and 24.2, and the counterforce 23 'with the force of the feedback spring 22' in equilibrium.
  • the control valve 16 in his in the Figure 3 illustrated rest position. If the control signal for the proportional magnet 24.1 or 24.2 is changed, the valve piston is displaced either in the direction of a first end position or the second end position due to the force imbalance.
  • the control pressure line 17 ' as already with reference to the Fig. 1 has been explained, either connected to the tank volume 7 or the control pressure source.
  • the connecting line 18 has no pressure reducing valve. However, this can also in the embodiment according to Fig. 3 be provided.
  • the arrangement of the second embodiment also has the advantage that only proportional leak pressure can reach the proportional solenoids. A pressure high-pressure resistant construction of the proportional magnets is therefore not required.
  • Matching elements are provided with matching reference numerals.
  • the changed elements were provided with primed reference numerals.
  • the Fig. 4 shows a partial section through an axial piston machine 40, in which the hydraulic system according to the invention finds application. Elements which have already been shown and explained in the schematic representations are designated correspondingly in the sectional representation. Their re-explanation will be omitted to avoid unnecessary repetition.
  • the axial piston machine 40 has a pivoting cradle 41 for adjusting its delivery or absorption volume. This pivoting cradle is tiltable with respect to its inclination angle relative to the axis of rotation of a drive shaft of the axial piston machine 40. To adjust the inclination angle, the pivoting cradle 41, which forms the adjusting mechanism of the hydraulic machine, can be acted upon by thrust forces generated by the first actuating piston 8 and the second actuating piston 9.
  • the position of the pivoting cradle 41 and thus of the set delivery or displacement volume of the axial piston machine 40 is fed back to the control valve 16 by means of the return lever 31.
  • the return lever 31 acts on a movably arranged spring bearing 42.
  • the feedback spring 22 ' is supported, and acts in the manner already described on the control valve 16'.
  • the spring bearing 42 is penetrated by a transmission element 43, by means of which the thrust force generated by the second proportional magnet 24.2 is transmitted to the valve piston of the control valve 16 '.
  • Spring bearing 42 and transmission element 43 do not touch each other.
  • valve piston 44 of the control valve 16 ' can be seen, which is arranged longitudinally displaceable in a valve sleeve. At its first end a spring plate is arranged, on which the feedback spring 22 'is supported. The valve piston 44 is thus acted upon via the spring plate with the force of the feedback spring 22 '. In the opposite direction acts on the valve piston 44, the counterforce generated by the spring 23 '.
  • a pair of proportional magnets 24.1 and 24.2 is provided as the actuating means in this embodiment.
  • the counterforce generating spring 23 ' is received in a valve piston 44 towards the open sleeve 51, the outside of which is conical in shape and rests against a screwed into the valve sleeve 52 adjusting pin.
  • the sleeve 51 can be moved axially and thus the force of the spring 23 'can be adjusted.
  • a lock nut 53 By a lock nut 53, the position of the adjusting pin 52 is secured.
  • the rest position of the adjusting mechanism is adjustable with vanishing control force.
  • control valve can also be actuated hydraulically, wherein different high forces are exerted on the valve piston by different high control pressures.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Compressor (AREA)

Claims (15)

  1. Système hydraulique avec une machine hydrostatique (2) avec un mécanisme de réglage réglable, avec un dispositif de réglage interagissant avec le mécanisme de réglage comportant au moins un piston de réglage (8) délimitant une chambre de pression de réglage (12) et avec une soupape de réglage (16, 16') avec laquelle l'amenée et l'évacuation de moyen de pression dans et hors de la chambre de pression de réglage (12) peuvent être commandées pour faire coulisser le piston de réglage (8), la soupape de réglage (16) comportant un piston de soupape sollicité par une force d'un ressort de rappel (22, 22') dépendant de la position du mécanisme de réglage, caractérisé en ce que le piston de soupape (44) est en outre sollicité par une contre-force agissant contre la force du ressort de rappel (22, 22') et que des moyens d'actionnement (24, 24.1, 24.2) sont prévus à l'aide desquels le piston de soupape peut être sollicité par une force de commande agissant dans le même sens que la contre-force ou agissant à l'encontre de la contre-force.
  2. Système hydraulique selon la revendication 1, caractérisé en ce qu'un ressort (23, 23') sollicitant le piston de soupape (44) à l'encontre du ressort de rappel (22, 22') est utilisé pour produire la contre-force.
  3. Système hydraulique selon la revendication 1 ou 2, caractérisé en ce que la force de commande est réglable en permanence.
  4. Système hydraulique selon l'une quelconque des revendications 1 à 3, caractérisé en ce que le moyen d'actionnement comporte un premier et un deuxième aimant proportionnel (24.1, 24.2) agissant dans des directions opposées sur le piston de soupape.
  5. Système hydraulique selon l'une quelconque des revendications 1 à 3, caractérisé en ce que le moyen d'actionnement comporte un aimant à double course (24) pourvu d'un premier enroulement et d'un deuxième enroulement pour produire la force de commande dans respectivement une des directions de force opposées.
  6. Système hydraulique selon l'une quelconque des revendications 1 à 5, caractérisé en ce que le ressort de rappel (22) est disposé entre le piston de réglage (8) et le piston de soupape.
  7. Système hydraulique selon l'une quelconque des revendications 1 à 3, caractérisé en ce que la machine hydrostatique (2) est réglée sur un volume d'extraction différent de zéro lorsque la force de commande faible diminue et que l'équilibre des forces entre la contre-force et la force dépendant de la position du mécanisme de réglage est atteint.
  8. Système hydraulique selon l'une quelconque des revendications 1 à 7, caractérisé en ce que le dispositif de réglage comporte en outre un piston de réglage (9) supplémentaire qui sollicite le mécanisme de réglage de façon opposée par rapport au piston de réglage (8) délimitant la chambre de pression de commande (12).
  9. Système hydraulique selon la revendication 8, caractérisé en ce que le ressort de rappel (22') est disposé entre le piston de réglage (9) supplémentaire et le piston de soupape (44).
  10. Système hydraulique selon l'une quelconque des revendications 1 à 9, caractérisé en ce qu'une source de pression de réglage est reliée à la soupape de réglage (16, 16') par le biais d'une conduite de liaison (18, 18') et qu'une soupape de réduction de pression (21) est disposée dans la conduite de liaison (18).
  11. Système hydraulique selon la revendication 10, caractérisé en ce que la source de pression de réglage est une conduite de travail (3) de la machine hydrostatique (2) ou une source de moyen de pression (20) supplémentaire, la conduite de travail (3) ou la source de moyen de pression (20) supplémentaire étant reliée à la conduite de liaison (18) par le biais d'un clapet navette (19).
  12. Système hydraulique selon la revendication 10, caractérisé en ce que la chambre de pression de réglage (12) délimitée dans une première position d'extrémité de la soupape de réglage (16, 16') par la surface de piston de réglage (14) du piston de réglage (8) est reliée à la source de pression de réglage.
  13. Système hydraulique selon la revendication 12, caractérisé en ce que la première chambre de pression de réglage (12) délimitée dans une deuxième position d'extrémité opposée de la soupape de réglage (16, 16') par la surface de piston de réglage (14) du piston de réglage (8) est reliée à un volume de réservoir (7).
  14. Système hydraulique selon la revendication 13, caractérisé en ce que la chambre de pression de réglage (12) délimitée, dans une position neutre prévue entre la première position d'extrémité et la deuxième position d'extrémité de la soupape de réglage (16, 16'), par la surface de piston de réglage (14) du piston de réglage (8) est reliée de façon étranglée avec le volume de réservoir (7) et de façon étranglée avec la source de pression de réglage.
  15. Système hydraulique selon l'une quelconque des revendications précédentes, caractérisé en ce que le ressort de rappel (22') est disposé entre une partie de transmission (31) fixée à un piston de réglage (9) et le piston de soupape (44).
EP08801632A 2007-08-20 2008-08-20 Système hydraulique avec une machine hydrostatique réglable Not-in-force EP2179176B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007039173 2007-08-20
PCT/EP2008/006851 WO2009024337A1 (fr) 2007-08-20 2008-08-20 Système hydraulique à machine hydrostatique réglable

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EP2179176A1 EP2179176A1 (fr) 2010-04-28
EP2179176B1 true EP2179176B1 (fr) 2013-04-03

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EP08801631A Not-in-force EP2179175B1 (fr) 2007-08-20 2008-08-20 Machine à piston axial du type à plateau oscillant, présentant un dispositif de réglage
EP08801632A Not-in-force EP2179176B1 (fr) 2007-08-20 2008-08-20 Système hydraulique avec une machine hydrostatique réglable

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EP08801631A Not-in-force EP2179175B1 (fr) 2007-08-20 2008-08-20 Machine à piston axial du type à plateau oscillant, présentant un dispositif de réglage

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US (2) US8006610B2 (fr)
EP (2) EP2179175B1 (fr)
JP (1) JP5027303B2 (fr)
CN (2) CN101815865B (fr)
DE (2) DE102008038435A1 (fr)
WO (2) WO2009024337A1 (fr)

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Publication number Publication date
US20100206161A1 (en) 2010-08-19
EP2179175A1 (fr) 2010-04-28
WO2009024337A1 (fr) 2009-02-26
DE102008038455A1 (de) 2009-02-26
JP5027303B2 (ja) 2012-09-19
CN101815865B (zh) 2012-06-27
US20100199838A1 (en) 2010-08-12
DE102008038435A1 (de) 2009-02-26
CN101842590B (zh) 2012-12-05
CN101842590A (zh) 2010-09-22
EP2179175B1 (fr) 2013-02-27
CN101815865A (zh) 2010-08-25
US8006610B2 (en) 2011-08-30
JP2010537108A (ja) 2010-12-02
WO2009024336A1 (fr) 2009-02-26
EP2179176A1 (fr) 2010-04-28

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