EP2179176A1 - Hydraulisches system mit einer verstellbaren hydrostatischen maschine - Google Patents
Hydraulisches system mit einer verstellbaren hydrostatischen maschineInfo
- Publication number
- EP2179176A1 EP2179176A1 EP08801632A EP08801632A EP2179176A1 EP 2179176 A1 EP2179176 A1 EP 2179176A1 EP 08801632 A EP08801632 A EP 08801632A EP 08801632 A EP08801632 A EP 08801632A EP 2179176 A1 EP2179176 A1 EP 2179176A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- piston
- control
- valve
- force
- hydraulic system
- 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
- 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.
- DE 199 49 169 C2 discloses a hydrostatic system with an adjustable hydraulic pump arranged in an open circuit.
- 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 proposed hydrostatic system allows due to the arrangement of the feedback spring on the one hand and the proportional solenoid on the other hand, a simple integration into a pump unit.
- a center position of the actuating piston is not possible with vanishing control signal and a variable in two opposite directions hydrostatic machine can only be brought by generating a control force by the proportional solenoid in its neutral position.
- 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.
- Adjustment device with vanishing control signal the adjusting device are deflected in two opposite directions.
- the hydrostatic system according to the invention therefore has the advantage that not only an adjustment of a hydraulic pump between e.g. one
- Brake energy recovery devices used can be controlled in a simple manner.
- advantageous developments of the hydraulic system according to the invention are carried out.
- 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.
- Stelldruckraum 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.
- a control pressure source for example, of different
- 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.
- Actuating mechanism of the hydrostatic machine is clamped at any time hydraulically. Nevertheless, the maximum possible actuating pressures of the first actuating piston are reduced compared to the actual working pressure. In particular, thereby the actuating means, but also the control valve is only exposed to a lower pressure load.
- 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 a control 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.
- 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. In this neutral position of the control valve, 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 connected to the actuating 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.
- FIG. 1 Line schematic representation of a first embodiment of the hydraulic system according to the invention using the example of a device for braking energy recovery;
- FIG. 2 shows a schematic illustration to illustrate the proportional adjustment of the stroke volume of the hydrostatic machine as a function of a first and a second control signal
- FIG. 3 is a schematic representation of a modified embodiment of the hydraulic system according to the invention, with a control valve actuated by two proportional solenoids;
- Fig. 4 is a sectional view of an exemplary
- Axial piston machine which is built according to the system according to the invention.
- Fig. 5 is a sectional view through one of two
- 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 pump In order to operate the hydrostatic machine 2 as a pump, is 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.
- Hydraulic accumulator 6 generates an output torque via the hydrostatic machine 2, which is supplied to the acceleration of the vehicle to the drive train.
- the hydraulic accumulator 6 is emptied into the tank volume 7 via the first working line 3, the hydrostatic machine 2 and the second working line 4.
- 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 help of the shuttle valve 19 is as a control pressure source either the first working line 3 or another
- a pressure reducing valve 21 is provided in the connecting line 18.
- 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. In the opposite direction acts on the pressure reducing valve 21, 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.
- Spring 23 is made adjustable, so that the position of the first actuating piston 8, in which the valve piston in an equilibrium of forces between the
- 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.
- 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 in a section between the shuttle valve 19 and the
- Pressure reducing valve 21 connected to the second control pressure chamber 13.
- the hydrostatic machine 2 is adjusted until a force equilibrium 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. By reducing the pressure by means of the pressure reducing valve 21, the load on the actuator 24 is reduced.
- This actuator 24 is designed as Doppelhubmagnet with two windings. 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. This is when the actuator 24 by means of the first
- Winding a control force in a first direction of force which acts in the same direction with the opposing force of the spring 23 on the valve piston generates.
- 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 actuator 24 is driven in the direction of the first direction of force, the valve piston is adjusted in the direction of its second end position.
- the first control pressure chamber 12th relaxed via the control pressure line 17 into the tank volume 7.
- the hydraulic force on the first control piston 8 is reduced. Since an unchanged pressure prevails in the second control pressure chamber 13 at the same time, the force on the second control piston 9 is not reduced. Due to the force imbalance, an adjustment of the first actuating piston 8 in FIG. 1 to the right.
- the force of the feedback spring 22 increases to the first end of the valve piston, until again a balance of forces between the force of the feedback spring 22 and the resultant of the control force of the actuator 24 and the opposing force of the spring 23 prevails.
- Actuator 24 a thrust force against the spring 23 are generated and the bias of the spring 23 to the valve piston is relieved. Due to the resulting smaller, acting on the second end of the valve piston resultant, the valve piston is adjusted in the direction of its first end position. In the first end position of the control valve 16, the connecting line 18 is connected to the control pressure line 17, so that the first control pressure chamber 12 is supplied from the control pressure source pressure medium. Due to the area ratios, the hydraulic force acting on the first actuating piston 8 is thus greater than the hydraulic force acting on the second actuating piston, so that an adjustment of the first actuating piston 8 in FIG. 1 takes place to the left. This reduces the force generated by the feedback spring 22 on the valve piston at the first end.
- the movement of the first actuating piston 8 takes place in each case until, again, a balance of forces has set between the resultant and the force of the feedback spring 22 and the control valve is again in the rest position shown in FIG.
- 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 driving elements 27, 27 ' bias the first return spring 25.
- the first return spring 25 is supported on a displaceably arranged spring plate 28 from.
- This is displaceable on the linkage and is based on a movement to the right of the housing side.
- an adjusting movement in which the first adjusting piston 8 is moved to the right in FIG. 1, 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 '.
- 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.
- Carrying elements 27, 27 'and 30, 30' the assembly is greatly simplified, since a pre-assembly can take place.
- Machine 2 as a pump or the intake volume V ⁇ at
- Adjusting 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
- a pressure of about 1/3 of the working pressure is required to achieve an equilibrium of forces between the two actuating pistons 8.9.
- By adjusting the pressure reducing valve to 2/3 of the working pressure is thus a sufficient pressure reserve for pivoting the hydrostatic machine 2 in the direction of engine operation available.
- Fig. 3 shows a modified embodiment. The function substantially coincides with the function explained with reference to FIG. 1, for which reason only the changes from the first exemplary embodiment will be discussed below. in 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 ' makes it possible to provide a first proportional magnet 24.1 and a second proportional magnet 24.2 as the actuating means instead of the Doppelhubmagneten 24, as used in FIG.
- 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 '. Since the first adjusting piston 8 and the second adjusting piston 9 via the adjusting mechanism of the hydraulic pump 2, i. d. R.
- a pivoting cradle are mechanically coupled to one another, a tapping of the position of the adjusting mechanism via the connection between the second adjusting piston 9 and the adjusting mechanism of the hydraulic machine 2 can take place. 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 has already been explained with reference to FIG. 1, a counterforce, 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.
- Proportional magnet 24.1 or a thrust force through the second proportional magnet 24.2 on opposite end faces of the valve piston are Proportional magnet 24.1 or a thrust force through the second proportional magnet 24.2 on opposite end faces of the valve piston.
- 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 ' is in its rest position shown in FIG. 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 actuating pressure line 17 ' is connected to either the tank volume 7 or the control pressure source.
- the illustrated embodiment the
- Connecting line 18 no pressure reducing valve on may also be provided in the embodiment of FIG. 3.
- 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. In order to clarify the similarity of the hydraulic system, the changed elements were provided with primed reference numerals.
- 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 to adjust their beneficiat. Swallowing volume on a pivoting cradle 41. 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 is the pivoting cradle 41, the
- Adjusting mechanism of the hydraulic machine forms can be acted upon by the first actuating piston 8 and the second actuating piston 9 generated thrust forces.
- 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 on the spring bearing 42 and acts on the control valve 16 "in the manner already described.
- 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 acts on the valve piston of the control valve 16 'is transmitted. Spring bearing 42 and transmission element 43 do not touch each other.
- FIG. 16 An enlarged view of the control valve 16 'is shown in FIG.
- valve piston 44 of the control valve 16 ' can be seen, which is arranged longitudinally displaceable in a valve sleeve.
- a spring plate is arranged, on which the
- the control pressure line 17' is throttled with the connecting line 18 and connected to the tank volume 7.
- the first control pressure chamber 12 therefore acts a mean pressure.
- holes 45, 46 are provided in the valve sleeve, which communicate with each other and with the spring chamber 47.
- the return arm 38 of the spring chamber 47 With the Housing volume of the axial piston engine 40 connected, which thus forms the tank volume.
- control edges release an unthrottled or virtually unthrottled connection between the actuating pressure line 17 'and in each case one of two annular spaces formed around the valve piston 44.
- the annular space oriented closer to the first proportional magnet 24.1 stands in permanent connection with the bore 45 and thus with the tank volume 7.
- the annular space arranged on the side facing the second proportional magnet 24.2 is permanently connected to the connecting line 18.
- 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.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102007039173 | 2007-08-20 | ||
PCT/EP2008/006851 WO2009024337A1 (de) | 2007-08-20 | 2008-08-20 | Hydraulisches system mit einer verstellbaren hydrostatischen maschine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2179176A1 true EP2179176A1 (de) | 2010-04-28 |
EP2179176B1 EP2179176B1 (de) | 2013-04-03 |
Family
ID=39884939
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08801632A Not-in-force EP2179176B1 (de) | 2007-08-20 | 2008-08-20 | Hydraulisches system mit einer verstellbaren hydrostatischen maschine |
EP08801631A Not-in-force EP2179175B1 (de) | 2007-08-20 | 2008-08-20 | Axialkolbenmaschine in schrägscheibenbauweise mit einer stellvorrichtung |
Family Applications After (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08801631A Not-in-force EP2179175B1 (de) | 2007-08-20 | 2008-08-20 | Axialkolbenmaschine in schrägscheibenbauweise mit einer stellvorrichtung |
Country Status (6)
Country | Link |
---|---|
US (2) | US20100199838A1 (de) |
EP (2) | EP2179176B1 (de) |
JP (1) | JP5027303B2 (de) |
CN (2) | CN101842590B (de) |
DE (2) | DE102008038435A1 (de) |
WO (2) | WO2009024336A1 (de) |
Families Citing this family (39)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102006062065A1 (de) * | 2006-12-29 | 2008-07-03 | Robert Bosch Gmbh | Axialkolbenmaschine mit einem einen radial erweiterten Innenraumabschnitt aufweisenden Gehäuse |
JP5410427B2 (ja) * | 2007-08-07 | 2014-02-05 | ローベルト ボッシュ ゲゼルシャフト ミット ベシュレンクテル ハフツング | 調整バルブを制御するためのリターン要素を有する制御装置を有する液圧機械 |
WO2012010137A2 (de) * | 2010-07-08 | 2012-01-26 | Robert Bosch Gmbh | Hydraulische doppelaxialkolbenmaschine |
DE102011105544A1 (de) * | 2010-07-08 | 2012-01-12 | Robert Bosch Gmbh | Hydraulische Axialkolbenmaschine |
DE102010032649A1 (de) | 2010-07-29 | 2012-02-02 | Robert Bosch Gmbh | Verstellbare Axialkolbenmaschine und Schwenkwiege |
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DE102011006102A1 (de) | 2011-03-25 | 2012-09-27 | Zf Friedrichshafen Ag | Stellvorrichtung eines Hydrostatmoduls |
WO2013037582A1 (de) | 2011-09-16 | 2013-03-21 | Robert Bosch Gmbh | Versteileinrichtung für eine hydrostatische maschine und hydrostatische maschine |
DE102011117543A1 (de) | 2011-11-03 | 2013-05-08 | Robert Bosch Gmbh | Axialkolbenmaschine |
DE102011121520A1 (de) | 2011-12-16 | 2013-06-20 | Robert Bosch Gmbh | Verstelleinrichtung für eine Axialkolbenmaschine undAxialkolbenmaschine mit einer Verstelleinrichtung |
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DE102012104755A1 (de) * | 2012-06-01 | 2013-12-05 | Linde Hydraulics Gmbh & Co. Kg | Hydrostatische Verdrängermaschine |
GB2502824A (en) * | 2012-06-08 | 2013-12-11 | Water Hydraulics Company Ltd | Axial piston variable stroke hydraulic machine |
DE102012015503A1 (de) | 2012-08-04 | 2014-02-06 | Robert Bosch Gmbh | Hydrostatische Axialkolbenmaschine |
DE102012214373A1 (de) | 2012-08-13 | 2014-05-15 | Robert Bosch Gmbh | Hydrostatische Axialkolbenmaschine |
DE102013214861A1 (de) * | 2012-08-16 | 2014-05-22 | Robert Bosch Gmbh | Verstellvorrichtung für eine hydrostatische Pumpe und hydrostatische Pumpe |
DE102012021320A1 (de) * | 2012-10-31 | 2014-04-30 | Robert Bosch Gmbh | Verstellvorrichtung für eine hydrostatische Kolbenmaschine und hydrostatische Kolbenmaschine mit einer derartigen Verstellvorrichtung |
DE102012022694A1 (de) | 2012-11-20 | 2014-05-22 | Robert Bosch Gmbh | Regelventil, insbesondere für eine elektroproportionale Schwenkwinkelregelung einer Hydromaschine |
DE102012023272A1 (de) | 2012-11-29 | 2014-06-05 | Robert Bosch Gmbh | Verstelleinrichtung für eine hydraulische Axialkolbenmaschine und hydraulische Axialkolbenmaschine |
DE102013202615A1 (de) | 2013-02-19 | 2014-08-21 | Robert Bosch Gmbh | Verstellbare Hydromaschine |
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US9664184B2 (en) * | 2013-05-22 | 2017-05-30 | Hydac Drive Center Gmbh | Axial piston pump having a swash-plate type construction |
DE102013212199A1 (de) | 2013-06-26 | 2014-12-31 | Robert Bosch Gmbh | Adaptiver Ansatz zur Regelung einer Axialkolbeneinheit mit EP-Verstellung |
DE102013213883A1 (de) * | 2013-07-16 | 2015-01-22 | Robert Bosch Gmbh | Verfahren und System zum Regeln eines Schwenkwinkels |
DE102013216395B4 (de) * | 2013-08-19 | 2019-01-17 | Danfoss Power Solutions a.s. | Steuereinrichtung für hydraulische verstellpumpen und verstellpumpe mit einer steuereinrichtung |
DE102013225899A1 (de) | 2013-12-13 | 2015-06-18 | Robert Bosch Gmbh | Schrägscheibenmaschine, Schrägscheibe und Verfahren zur hydrostatischen Entlastung einer Stellteilanbindung einer Schrägscheibenmaschine |
DE102013225892A1 (de) | 2013-12-13 | 2015-06-18 | Robert Bosch Gmbh | Schrägscheibenmaschine, Schrägscheibe und Verfahren zur hydrostatischen Entlastung einer Stellteilanbindung einer Schrägscheibenmaschine und zum Druckabbau eines Arbeitsmediums während eines Umsteuervorgangs der Schrägscheibenmaschine |
DE102014202413A1 (de) | 2014-02-11 | 2015-08-13 | Robert Bosch Gmbh | Elektrisch angesteuertes Regelventil für eine verstellbare hydrostatische Pumpe und verstellbare hydrostatische Pumpe |
DE102015202406A1 (de) | 2014-02-18 | 2015-08-20 | Robert Bosch Gmbh | Hydraulische Anordnung |
DE102014211194A1 (de) * | 2014-06-12 | 2015-12-17 | Robert Bosch Gmbh | Hydrostatische Axialkolbenmaschine in Schrägscheibenbauweise und Lüfter mit einer hydrostatischen Axialkolbenmaschine |
CA3005333A1 (en) * | 2015-11-15 | 2017-05-18 | Eaton Intelligent Power Limited | Hydraulic pump control system |
DE102015224129A1 (de) * | 2015-12-03 | 2017-06-08 | Robert Bosch Gmbh | Hydrostatische Axialkolbenmaschine |
CH714321A1 (de) * | 2017-11-11 | 2019-05-15 | Liebherr Machines Bulle Sa | Verstellvorrichtung für eine Axialkolbenmaschine. |
FR3093138B1 (fr) * | 2019-02-25 | 2022-07-15 | Univ Versailles Saint Quentin En Yvelines | Actionneur hydraulique à compensation de surpression |
CN112343806B (zh) * | 2019-08-08 | 2023-08-29 | 丹佛斯动力系统公司 | 用于开放回路可变排量泵的电动排量控制 |
US11644028B2 (en) * | 2020-04-08 | 2023-05-09 | Danfoss Power Solutions, Inc. | Control arrangement for variable displacement pump |
CN114382609A (zh) * | 2021-12-13 | 2022-04-22 | 天津大学 | 往复式高低压自适应补偿密封装置 |
FR3131273A1 (fr) * | 2021-12-23 | 2023-06-30 | Safran Aircraft Engines | Circuit de commande hydraulique de calage d’aubes de soufflante |
FR3131274A1 (fr) * | 2021-12-23 | 2023-06-30 | Safran Aircraft Engines | Circuit de commande hydraulique de calage d’aubes de soufflante |
Family Cites Families (17)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3234889A (en) * | 1963-02-07 | 1966-02-15 | New York Air Brake Co | Hydraulic device |
DE3213958A1 (de) * | 1981-08-21 | 1983-03-03 | Robert Bosch Gmbh, 7000 Stuttgart | Elektrohydraulische verstelleinrichtung fuer eine hydrostatische maschine |
DE3733625A1 (de) * | 1987-07-23 | 1989-02-02 | Bosch Gmbh Robert | Axialkolbenmaschine |
EP0367476A1 (de) * | 1988-11-02 | 1990-05-09 | Vickers Systems Limited | Pumpen mit variabler Verdrängung |
JPH02140468A (ja) * | 1988-11-18 | 1990-05-30 | Daikin Ind Ltd | 可変容量形液圧装置 |
DE3935800C2 (de) * | 1989-10-27 | 1997-03-27 | Linde Ag | Einstellbare Axialkolbenmaschine in Schrägscheibenbauweise |
DE4203619C2 (de) * | 1992-02-07 | 1996-07-25 | Rexroth Mannesmann Gmbh | Hydrauliksystem |
DE4229007C2 (de) * | 1992-08-31 | 2002-06-13 | Linde Ag | Axialkolbenmaschine in Schrägscheibenbauweise |
DE19653165C2 (de) | 1996-12-19 | 2002-04-25 | Brueninghaus Hydromatik Gmbh | Verstelleinrichtung zur Verstellung des Fördervolumens einer Axialkolbenpumpe |
DE19705598A1 (de) | 1997-02-14 | 1998-08-20 | Bosch Gmbh Robert | Elektromechanischer Doppelhubmagnet |
US5794515A (en) * | 1997-04-03 | 1998-08-18 | Bethke; Donald G. | Swashplate control system for an axial piston pump |
DE19807443A1 (de) * | 1998-02-24 | 1999-08-26 | Kleinedler | Axialkolbenmaschine |
DE19949169C2 (de) | 1999-10-12 | 2001-10-11 | Brueninghaus Hydromatik Gmbh | Verstellvorrichtung |
DE10136416A1 (de) | 2001-07-26 | 2003-02-13 | Brueninghaus Hydromatik Gmbh | Ventilblock für eine Regelvorrichtung, insbesondere für eine hydrostatische Maschine |
US6705203B2 (en) * | 2001-11-28 | 2004-03-16 | Sauer-Danfoss Inc. | Extended male slipper servo pad arrangement for positioning swashplate and method assembling same |
DE10313426B3 (de) * | 2003-03-25 | 2004-11-11 | Sauer Bibus Gmbh | Verstellpumpeneinheit |
DE10325842A1 (de) * | 2003-06-06 | 2005-01-05 | Brueninghaus Hydromatik Gmbh | Reversierbare Axialkolbenmaschine mit Längsverstellung |
-
2008
- 2008-08-20 WO PCT/EP2008/006850 patent/WO2009024336A1/de active Application Filing
- 2008-08-20 DE DE102008038435A patent/DE102008038435A1/de not_active Withdrawn
- 2008-08-20 EP EP08801632A patent/EP2179176B1/de not_active Not-in-force
- 2008-08-20 DE DE102008038455A patent/DE102008038455A1/de not_active Withdrawn
- 2008-08-20 EP EP08801631A patent/EP2179175B1/de not_active Not-in-force
- 2008-08-20 CN CN200880103668.1A patent/CN101842590B/zh not_active Expired - Fee Related
- 2008-08-20 JP JP2010521358A patent/JP5027303B2/ja not_active Expired - Fee Related
- 2008-08-20 WO PCT/EP2008/006851 patent/WO2009024337A1/de active Application Filing
- 2008-08-20 CN CN2008801027004A patent/CN101815865B/zh not_active Expired - Fee Related
-
2010
- 2010-02-22 US US12/710,131 patent/US20100199838A1/en not_active Abandoned
- 2010-02-22 US US12/710,050 patent/US8006610B2/en not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO2009024337A1 * |
Also Published As
Publication number | Publication date |
---|---|
US20100199838A1 (en) | 2010-08-12 |
EP2179176B1 (de) | 2013-04-03 |
DE102008038435A1 (de) | 2009-02-26 |
DE102008038455A1 (de) | 2009-02-26 |
EP2179175B1 (de) | 2013-02-27 |
CN101842590B (zh) | 2012-12-05 |
CN101815865B (zh) | 2012-06-27 |
WO2009024336A1 (de) | 2009-02-26 |
US20100206161A1 (en) | 2010-08-19 |
US8006610B2 (en) | 2011-08-30 |
JP5027303B2 (ja) | 2012-09-19 |
EP2179175A1 (de) | 2010-04-28 |
JP2010537108A (ja) | 2010-12-02 |
WO2009024337A1 (de) | 2009-02-26 |
CN101842590A (zh) | 2010-09-22 |
CN101815865A (zh) | 2010-08-25 |
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