EP1664530A1 - Dispositif de regulation de puissance - Google Patents

Dispositif de regulation de puissance

Info

Publication number
EP1664530A1
EP1664530A1 EP04764612A EP04764612A EP1664530A1 EP 1664530 A1 EP1664530 A1 EP 1664530A1 EP 04764612 A EP04764612 A EP 04764612A EP 04764612 A EP04764612 A EP 04764612A EP 1664530 A1 EP1664530 A1 EP 1664530A1
Authority
EP
European Patent Office
Prior art keywords
power control
throttle
control device
pressure
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP04764612A
Other languages
German (de)
English (en)
Other versions
EP1664530B1 (fr
Inventor
Karl-Heinz Blum
Harald Ludescher
Wolfgang Kauss
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.)
Brueninghaus Hydromatik GmbH
Original Assignee
Brueninghaus Hydromatik GmbH
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 Brueninghaus Hydromatik GmbH filed Critical Brueninghaus Hydromatik GmbH
Publication of EP1664530A1 publication Critical patent/EP1664530A1/fr
Application granted granted Critical
Publication of EP1664530B1 publication Critical patent/EP1664530B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/002—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
    • 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
    • F04B49/00—Control, e.g. of pump delivery, or pump pressure of, or safety measures for, machines, pumps, or pumping installations, not otherwise provided for, or of interest apart from, groups F04B1/00 - F04B47/00
    • F04B49/08—Regulating by delivery pressure

Definitions

  • the invention relates to a power control device for a hydrostatic piston machine.
  • a power control valve for power control in a hydrostatic piston machine, it is known from DE 100 01 826 Cl to use a power control valve in a recess formed on a housing of a hydrostatic piston machine, by means of which a control pressure acting in a control pressure chamber is regulated.
  • the actuating pressure chamber is formed within an actuating device which is located in the axial extension of the power control valve.
  • channels are formed at the end which open into the signal pressure chamber. Due to the actuating movement of the actuating piston, the actuating pressure chamber experiences a change in volume. The channels that connect the signal pressure chamber to the power control valve create a volume flow due to this volume change.
  • the actuating piston is acted upon by a spring force which acts in the direction of the smaller volume of the actuating pressure chamber.
  • the control pressure chamber is connected to a tank volume of the hydrostatic piston machine in the corresponding control state by the power control valve.
  • a throttle point is provided in the line which connects the power control valve to the tank volume, by means of which it is prevented that the actuating movement of the hydrostatic piston machine resulting from the spring loading of the actuating piston is too fast.
  • throttling is not provided in the feed line to the power control valve and in the connection between the steep pressure chamber and the power control valve.
  • a disadvantage of the known power control device is that the volume flow is only throttled late on the way of the pressure medium to the tank volume, as a result of which leakage in the power control valve and other pressure or volume control valves that may be present leads to the occurrence of a residual dynamic pressure upstream of the throttle comes, which has a negative impact on the control behavior of the power control device.
  • a throttle and a check valve arranged in parallel are provided in a connecting line that connects a control pressure chamber of the control device with an output adapter of a power control valve.
  • the check valve is closed so that the volume flow through the throttle point is limited and the actuating speed is thus reduced.
  • the check valve arranged in parallel allows the flow cross-section additionally released by the check valve to be used in the opposite direction, that is to say when the signal pressure chamber is depressed, so that a limitation of the volume flow does not occur, as a result of which correspondingly high positioning speeds are achieved.
  • the subclaims relate to advantageous developments of the power control device according to the invention.
  • the power control device is designed such that an increasing signal pressure adjusts the hydraulic pump in the direction of smaller delivery volume and the check valve is arranged such that it opens in the direction of the actuating device.
  • the throttle point and the check valve as a combined throttle check valve which comprises a throttle pin which is movable between two stops.
  • a combined throttle check valve which comprises a throttle pin which is movable between two stops.
  • FIG. 1 is a hydraulic circuit diagram for a power control device according to the invention
  • FIG. 2 shows a first exemplary embodiment of a power control device according to the invention
  • FIG. 3 shows a detail of a second exemplary embodiment of a power control device according to the invention
  • Fig. 4 is a partial section through a combined throttle check valve and
  • Fig. 5 is a schematic representation of an inventive arrangement of a check valve and a throttle point in an integrated power control valve.
  • the hydraulic pump unit 1 comprises a hydraulic pump 2, which conveys a pressure medium into a first working line 3, which it releases a second working line 4 sucks.
  • a power control device 5 is connected to an adjusting device of the hydraulic pump 2.
  • the adjusting device of the hydraulic pump 2 for example, adjusts the angle of a swivel plate of an axial piston machine.
  • the power control device 5 comprises an actuating cylinder 6, in which an actuating piston 7 is arranged, the actuating piston surface of which is struck in an actuating pressure chamber 8 with the force of an actuating pressure.
  • the power control device 5 has a power control valve 9 for setting the control pressure acting in the control pressure chamber 8.
  • An output port 10 of the power control valve 9 is connected to an actuating pressure chamber port 11 of the actuating cylinder 6 via a connecting line 12.
  • a combined throttle check valve 13 is provided in the connecting line 12 and consists of a throttle point 14 arranged in the connecting line 12 and a check valve 15 arranged in a bypass line 12 ′ formed parallel thereto.
  • the actuating piston 7 is acted upon by a return spring 16 with a force which acts on the actuating piston 7 against the actuating pressure acting in the actuating pressure chamber 8.
  • the hydraulic pump 2 is pivoted out in the direction of the maximum delivery volume in this position.
  • the power control valve 9 is designed as a 3/2-way valve which is infinitely adjustable between its two end positions.
  • the power control valve 9 has one in addition to the output port 10 Input connection 17, which is connected to the first working line 3 via a delivery pressure line 18.
  • the pressure generated by the hydraulic pump 2 in the first working line 3 is fed via the delivery pressure supply line 18 to the inlet connection 17, which is connected to the outlet connection 10 in a first end position of the power control valve 9. In this first end position, the steep pressure chamber 8 from the first working line 3 is pressurized with the delivery pressure prevailing in the first working line 3.
  • the pressure medium withdrawn from the first working line 3 via the delivery pressure supply line 18 is fed via the connecting line 12 to the control pressure chamber 8, whereby the check valve 15 opens in the combined throttle check valve 13 and thus an essentially unthrottled connection between the power control valve 9 and the control pressure chamber 8 via the bypass line 12 'is open.
  • the delivery pressure supply line 18 leads to the one delivery pressure measurement connection 19, at which the power control valve 9 is subjected to a force, so that it is deflected in the direction of its first end position, in which it causes the actuating pressure chamber 8 to be depressed.
  • the increase in the control pressure in the control pressure chamber 8 causes the control piston 7 to be shifted to the left in FIG. 1, such an adjustment movement corresponding to a reduction in the swivel angle of the hydraulic pump 2 and thus in the set delivery volume of the hydraulic pump 2.
  • the position of the valve piston arranged in the power control valve 9 is determined not only by the pressure applied to the delivery pressure measuring connection 19, but also by an oppositely acting force which is generated by a first compression spring 20.1 and a second, preferably adjustable compression spring 20.2.
  • the first and second compression springs 20.21.2 are supported on the one hand on the valve piston of the power control valve 9 and on the other hand on a coupling rod 21, so that the force counteracting the delivery pressure on the valve piston of the power control valve 9 increases with the set swivel angle becoming smaller and thus adjusts the power control valve 9 in the direction of its second end position.
  • the power control valve 9 is thus in an equilibrium position, which by the
  • Compression spring 20.1 and the second compression spring 20.2 is determined, the opposing force of the compression springs 20.1 and 20.2 depending on the set
  • the hydraulic pump 2 is increased by the movement of the actuating piston 7 to a smaller delivery volume and by the associated movement of the coupling rod 21, the force on the valve piston of the power control valve 9 in the direction of the second end position of the power control valve 9 is increased the connection between the input connection 17 and the output connection 10 is increasingly interrupted and at the same time a connection is established between the output connection 10 and a further connection 22.
  • the connection line 12 is connected to a tank volume 23 by this connection of the output connection 10 to the further connection 22.
  • the control pressure prevailing in the control pressure chamber 8 is thus relaxed via the connecting line 12 into the tank volume 23 and the control piston 7 is released the return spring 16 is adjusted so that the hydraulic pump 2 is adjusted in the direction of a larger swivel angle.
  • an expansion line 24 is provided in which a pressure limiting control valve 25 and a delivery volume control valve 26 are arranged.
  • the two valves form a section of the expansion line 24, through which flow can be flowed unthrottled.
  • an additional throttle 27 can be arranged in the expansion line 24, which can be made considerably larger in cross-section than in the known state of the art, so that the throttle 27 creates a residual dynamic pressure in the line region located upstream of the throttle 27 is prevented. A feedback of the throttling by the throttle 27 to the control behavior of the power control valve 9 is thus prevented. If necessary, the throttle 27 can also be omitted entirely.
  • the output port 10 and the further port 22 of the power control valve 9 are connected in addition to the inner, unthrottled connection in the second end position of the power control valve 9 outside the power control valve 9 via a bypass line 28 in which a second throttle 29 is arranged.
  • the output port 36 of the pressure limiting control valve 25 is connected via a second bypass line 100, in which a third throttle 101 and a fourth throttle 102 are arranged in series, to the relief line 24 downstream of the throttle 27 arranged therein.
  • a branch line 103 branches off from the second bypass line 100, the other end of which opens into a section of the expansion line 24 located between the further connection 35 of the pressure limiting control valve 25 and the output connection 40 of the delivery volume control valve 26. Leakage occurring at the power control valve 9 is discharged into the tank volume 23 via a leakage line 31.
  • the control range of the power control valve 9 is limited by the pressure limiting control valve 25 in the direction of excessively increasing pressure in the first working line 23.
  • the pressure limiting control valve 25 has a delivery pressure measuring connection 32, which, like an inlet connection 33 of the pressure limiting control valve 25, is connected to the first working line 3 via the delivery pressure supply line 18 and a delivery pressure supply line section 18 'branching therefrom.
  • the pressure limiting control valve 25 is located in the end position shown below a limit value which can be predetermined by an adjusting spring 34 and connects the further connection 35 of the pressure limiting control valve 25 to the output connection 36 of the pressure limiting control valve 25. Contrary to the force of the adjusting spring 34 engages.
  • the pressure limiting control valve 25 is adjusted in the direction of its second end position, in which the input port 33 of the pressure limiting control valve 25 is connected to the output port 36 of the pressure limiting control valve 25.
  • the further connection 22 of the power control valve 9 is thus acted upon by the delivery pressure, so that a relaxation of the control pressure chamber 8 is prevented by the increasing back pressure.
  • the actuating pressure chamber 8 is depressed via the pressure limiting control valve 25 and the hydraulic pump 2 is thus adjusted in the direction of smaller delivery volume, thus preventing a further pressure increase in the first working line 3.
  • Pressure limiting control valve 25 overridden.
  • the output control valve 9 can also be overridden by the delivery volume control valve 26.
  • the delivery pressure supplied via the delivery pressure supply line section 18 ′ is also at a delivery pressure measuring connection 37 of the delivery volume control valve 26 and at an inlet connection 38 of the delivery volume control valve 26 the first working line 3.
  • an operating pressure taken downstream of a delivery volume throttle 43 of the first working line 3 acts on a working pressure measuring port 42.
  • a working pressure supply line 44 branches off from the first working line 3 downstream of the delivery volume throttle 43.
  • the force acting on the valve piston of the delivery volume control valve 26 is dependent on the force of the adjustable delivery volume adjustment spring 41, with which the start of the delivery volume control valve 26 is set, and the difference in pressure in the first working line 3 upstream or downstream of the delivery volume throttle 43.
  • the valve piston of the delivery volume control valve 26 is brought in the direction of its second end position, in which the input port 38 of the delivery volume control valve 26 is connected to the output port 40 of the delivery volume control valve 26.
  • the pressure chamber 8 of the actuating device 5 is prevented from relaxing by interrupting the connection to the tank volume 23 and instead of it the further connection 22 of the power control valve 9 is connected to the input connection 38 of the delivery volume control valve 26.
  • the hydraulic pump 2 is adjusted in the direction of the smaller delivery volume.
  • critical operating situations can e.g. B. arise when a consumer is blocked, which leads to an increase in pressure, or if a leak occurs downstream of the delivery volume measuring throttle 43.
  • auxiliary pump 45 When starting the system from the idle state, the hydraulic system is depressed by an auxiliary pump 45 via a feed line 46, the feeding in z. B. the first working line 3 via a valve system, not shown.
  • the suction side of the auxiliary pump 45 is connected to the second working line 4 via a suction line 47.
  • the auxiliary pump 45 can be designed, for example, as a gear pump, which is driven together with the hydraulic pump 2 via a drive shaft 48 which is constructed in several parts.
  • the actuating device 5 shows a constructive embodiment of an actuating device 5.
  • the actuating device 5 is designed so that it can be used as a cartridge in a corresponding recess in the housing of a piston engine.
  • the actuating piston 7 is slidably guided in this recess in the housing.
  • the actuating piston 7 has a cup-shaped geometry, in the interior of which the actuating pressure chamber 8 is formed.
  • an extension 50 is formed in the interior of the cup-shaped geometry of the actuating piston 7, in which a threaded receptacle 51 is arranged, into which the coupling rod 21 is screwed.
  • the coupling rod 21 penetrates one Valve sleeve 52 and a valve piston 53, which cooperate as a power control valve 9.
  • the valve piston 53 has a spherical rounded portion 54, against which a first spring bearing 55 rests.
  • a contact surface for the first compression spring 20.1 and the second compression spring 20.2 are each formed on the first spring bearing 55.
  • the coupling rod which also extends through the first spring bearing 55
  • an external thread is arranged on the second spring bearing 57, onto which a third spring bearing 59 is screwed, on which the second compression spring 20.2 is supported.
  • the third spring bearing 59 is secured with a further lock nut 60.
  • the spring bearings 55, 57 and 59 as well as the first compression spring 20.1 and the second compression spring 20.2 are arranged in a spring chamber 61 which is formed in a spring housing 63 which is screwed onto the valve sleeve 52 in a sealing manner with an O-ring.
  • the spring chamber 61 is connected to the further connection via a compensating channel 62
  • the compensation channel 62 is designed as a bore in the valve sleeve 52.
  • the valve piston 53 has a circumferential first groove 64 and a circumferential second groove 65. Is the Valve piston 53 in its position corresponding to the second end position of the power control valve 9, the second port 65 connects the further port 22 to the output port 10. Due to the pressure prevailing in the first groove 64, a force is exerted on the valve piston 53 in the axial direction. In order to generate this force, the opposite boundary surfaces of the first groove 64 are of different sizes. The different sizes of the surfaces are achieved by grading the valve piston 53 and the valve sleeve 52.
  • the axial force displaces the valve piston 53 against the force of the first and second compression springs 20.1 and 20.2.
  • the displacement of the valve piston 53 displaces the second groove 65 to such an extent that the connection between the further connection 22 and the output connection 10 is increasingly interrupted.
  • the first groove 64 overlaps the output connection 10, so that the input connection 17, which is not visible in FIG. 2, is increasingly connected to the output connection 10.
  • the channel which forms the outlet connection 10 in the valve sleeve 52 is connected to the channel which forms the further connection 22 in the valve sleeve 52 by an axial bore, the narrowest cross section of which forms the bypass throttle 29.
  • the actuating device 5 is preferably used as an assembly group in a housing of a piston machine.
  • a first connecting channel 12.1 and a second connecting channel 12.2 are also introduced into the housing of the piston machine.
  • the first connection channel 12.1 and the second connection channel 12.2 are each closed on the outside of the housing by a plug 66.
  • the first connection channel 12.1 opens out on the side of the actuating device 5 in such a way that it is connected to the output connection 10.
  • the second connection channel 12.2 opens out in such a way that a connection with the control pressure chamber 8 is established.
  • a plurality of connection openings 68 can be arranged on the actuating piston 7, for example, distributed over the circumference of the actuating piston 7.
  • the adjusting piston 7 is preferably provided with a circumferential recess 67 on its outer circumference.
  • the first connecting channel 12.1 and the second connecting channel 12.2 are supplemented by a receiving opening 69 to the connecting line 12, in which the combined throttle check valve 13 is arranged.
  • the receiving opening 69 can be formed, for example, as a blind hole in the housing of the piston machine, an internal thread being formed at least over part of the length of the blind hole.
  • a first housing insert part 70 and a second housing insert part 71 are screwed into the receiving opening 69.
  • the first housing insert 70 and the throttle pin 72 are first inserted into the receiving opening 69.
  • the second housing insert 71 is then screwed into the receiving opening 69 before the receiving opening 69 is also closed with a sealing plug 66.
  • the throttle pin 72 has a conical part which cooperates with a stop to form a throttle point and is freely movable between two stops. Depending on the pressure drop, the throttle pin 72 is held in contact with one stop or the other stop. Thus, either a throttling cross section is released between the throttle pin 72 and the one stop, or a larger cross section is released, which produces an unthrottled or only slightly throttled connection between the first connecting channel 12.1 and the second connecting channel 12.2.
  • FIG. 3 A second embodiment is shown in FIG. 3. It can be seen here that a valve receptacle 74 in the form of a recess in the housing 73 is arranged in a housing 73 of the piston machine, into which the actuating device 5 is inserted with part of its length.
  • the actuating piston 7 of the actuating device 5 actuates a swash plate 75 due to its actuating movement, with which the delivery volume of the hydrostatic piston machine is adjusted.
  • a mounting surface 76 is formed, to which a housing 77 of the throttle check valve 13 is attached.
  • the housing 77 of the throttle check valve 13 is fastened to the housing 73 of the axial piston machine by means of screws 78.
  • a first housing channel 79.1 and a second housing channel 79.2 are introduced into the housing 73 and connect the valve receptacles 74 to the first connecting channel 12.1 and the second connecting channel 12.2, which in turn are provided in the housing 77 of the throttle check valve 13.
  • the first and second housing channels 79.1 and 79.2 thus form the connecting channel 12 together with the first connecting channel 12.1 and the second connecting channel 12.2 as well as the receiving opening 69 connecting the two connecting channels 12.1 and 12.2.
  • FIG Power control valve 9 shown.
  • the components of the second exemplary embodiment of FIG. 3 which are essentially identical to the components of the exemplary embodiment from FIG. 2 already described are provided with the same reference numerals. In order to avoid unnecessary repetitions, the description is not repeated.
  • a lubrication channel 80 is introduced on the outer circumference of the piston shaft of the actuating piston 7, which is connected to the actuating pressure chamber 8 via at least one lubrication bore 81.
  • the control pressure prevailing in the control pressure chamber 8 ensures a low leakage flow in the gap formed between the control piston 7 and the valve seat 74, which serves to lubricate the control piston 7 slidably arranged in the valve seat 74.
  • a locking ring 82 is inserted in the actuating piston 7, which, like a disk 83 lying thereon, is penetrated by the coupling rod 21.
  • a support body 84 is supported on the disk 83 and has a depression corresponding to a spherical head 85.
  • the spherical head 85 is connected to the coupling rod 21 and is supported on the actuating piston 7 on the side facing away from the recess of the support body 84, so that both tensile and thrust forces can be transmitted between the coupling rod 21 and the actuating piston 7.
  • a first recess 86 is arranged in the first housing insert part 70 and is embodied in steps.
  • the recess 86 is preferably rotationally symmetrical and penetrates the housing insert 70.
  • the at least one radial extension of the recess 86 forms a first stop 87 against which a cylindrical part 88 of the throttle pin 72 abuts when the throttle check valve 13 is in its open position.
  • the cylindrical part 88 has a diameter that is larger than the radially non-expanded part of the recess 86, but smaller than the radially expanded part of the recess 86, so that between the outer surface of the cylindrical part 88 of the throttle pin 72 and the first housing insert part 70 a gap 91 is formed.
  • a transverse bore 89 and a longitudinal bore 90 connected to it from the end face of the cylindrical part 88 are provided in the cylindrical part 88.
  • the recess 86 On the side of the first housing insert 70, on which the radially widened region of the recess 86 opens, the recess 86 is followed by a second recess 92, which in turn is preferably rotationally symmetrical in the second housing insert 71 and penetrates it.
  • the second recess 92 also has at least one radial step, which forms a second stop 93, which is oriented opposite to the first stop 87. In the direction of the second stop 93, a frustoconical part 94 adjoins the cylindrical part 88 of the throttle pin 72.
  • the diameter of the radially non-expanded area of the second recess 92 is dimensioned such that the throttle pin 72 with the conical part 94 partially extends into the radially non-expanded area of the second Recess 92 can dip, so that the outer surface of the truncated cone comes into contact with the inner peripheral edge of the second stop 93.
  • a plurality of flats 95 are formed on the circumference of the frustoconical part 94. Because of the flats 95, the throttle pin 72 cannot form a sealing seat on the second stop 93, but rather forms a throttle point, the cross section of which is preferably determined by the geometry of the flats 95. In the radially widened area of the second housing insert 71, the gap 91 formed between the throttle pin 72 and the first housing insert 70 is continued.
  • a throttling cross-section instead of the flats 95 on the conical part 94 of the throttle pin 72 z. B. notches on the second stop 93 may be present.
  • the throttle pin 72 can be exchanged for another throttle pin after the second housing insert 71 has been unscrewed from the housing (not shown in FIG. 4). This means that when using different flats on the throttle pins, the throttle point that is formed can be individually set.
  • a limiting cross section for example the longitudinal bore 90, it is also possible to achieve a throttling effect when the check valve 15 is open and thus not only adjust the pivoting out of the piston machine in the direction of the larger pivoting angle, but also the pivoting back to smaller pivoting angles.
  • FIG. 5 again shows a schematic illustration of the exemplary embodiment from FIG. 3, in which, however, a channel is provided in the valve sleeve 52 as the connection point for the connecting line 12.
  • the connection to the actuating pressure chamber 8 can thus simply be designed as a bore 99 in the valve sleeve 52 which extends in the axial direction.
  • Piston engine a first housing channel 79.1 and a second housing channel 79.2 provided which connect the valve receptacles 74 to the outside of the housing 73.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Reciprocating Pumps (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Safety Valves (AREA)

Abstract

L'invention concerne un dispositif de régulation de puissance destiné à une machine à pistons hydrostatique dont le volume de déplacement peut être modifié à l'aide d'un dispositif de réglage (5). Une pression de réglage agissant dans le dispositif de réglage (5) est régulée à l'aide d'une soupape de régulation de puissance (9) connectée au dispositif de réglage (5) par l'intermédiaire d'une ligne de connexion (12). Ladite ligne de connexion (12) contient une soupape antiretour (15) et une zone d'étranglement (14) disposée parallèlement à ladite soupape.
EP04764612A 2003-09-08 2004-08-30 Dispositif de regulation de puissance Expired - Lifetime EP1664530B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10341331A DE10341331B3 (de) 2003-09-08 2003-09-08 Leistungsregelvorrichtung
PCT/EP2004/009643 WO2005028863A1 (fr) 2003-09-08 2004-08-30 Dispositif de regulation de puissance

Publications (2)

Publication Number Publication Date
EP1664530A1 true EP1664530A1 (fr) 2006-06-07
EP1664530B1 EP1664530B1 (fr) 2007-10-03

Family

ID=34352772

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04764612A Expired - Lifetime EP1664530B1 (fr) 2003-09-08 2004-08-30 Dispositif de regulation de puissance

Country Status (4)

Country Link
US (1) US20060254269A1 (fr)
EP (1) EP1664530B1 (fr)
DE (2) DE10341331B3 (fr)
WO (1) WO2005028863A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011076581A1 (de) 2010-12-23 2012-06-28 Robert Bosch Gmbh Hydrostatische Kolbenmaschine mit Bremsvorrichtung
JP6021226B2 (ja) * 2013-11-28 2016-11-09 日立建機株式会社 建設機械の油圧駆動装置
DE102014206755B4 (de) 2014-02-18 2024-09-19 Robert Bosch Gmbh Verstelleinrichtung einer Axialkolbenmaschine mit einem Druckmittel beaufschlagten Steuerventil
DE102014211202A1 (de) * 2014-06-12 2015-12-17 Robert Bosch Gmbh Hydrostatische Axialkolbenmaschine in Schrägscheibenbauweise und Lüfter mit einer hydro-statischen Axialkolbenmaschine
EP3374639B1 (fr) 2015-11-15 2020-12-30 Eaton Intelligent Power Limited Système de commande de pompe hydraulique
CN110792584B (zh) * 2019-11-27 2021-06-08 力源液压（苏州）有限公司 一种柱塞泵的多档输入功率控制系统
CH717932A1 (de) * 2020-10-06 2022-04-14 Liebherr Machines Bulle Sa Hydraulische Ventileinheit, Leistungs- und/oder Drehmomentregelungssystem und Axialkolbenmaschine mit einer solchen.

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2121267A1 (de) * 1971-04-30 1972-11-16 G.L. Rexroth Gmbh, 8770 Lohr Verstellpumpe mit Verstellvorrichtung
SE396239B (sv) * 1976-02-05 1977-09-12 Hytec Ab Metod och anordning for reglering av den effekt som tillfors ett hydrauliskt, ett pneumatiskt eller ett hydraulpneumatiskt system
DE3345264A1 (de) * 1983-12-14 1985-06-27 Brueninghaus Hydraulik Gmbh, 7240 Horb Drehmomenten-regeleinrichtung fuer eine verstellbare hydropumpe
US4821514A (en) * 1987-06-09 1989-04-18 Deere & Company Pressure flow compensating control circuit
DE4302036C2 (de) * 1993-01-26 1996-07-11 Sauer Sundstrand Gmbh & Co Als Wechseldrossel ausgeführtes Steuerorgan
DE19949169C2 (de) * 1999-10-12 2001-10-11 Brueninghaus Hydromatik Gmbh Verstellvorrichtung
DE10001826C1 (de) * 2000-01-18 2001-09-20 Brueninghaus Hydromatik Gmbh Vorrichtung zum Regeln der Leistung einer verstellbaren Kolbenmaschine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2005028863A1 *

Also Published As

Publication number Publication date
EP1664530B1 (fr) 2007-10-03
US20060254269A1 (en) 2006-11-16
WO2005028863A1 (fr) 2005-03-31
DE10341331B3 (de) 2005-05-25
DE502004005162D1 (de) 2007-11-15

Similar Documents

Publication Publication Date Title
EP2179175B1 (fr) Machine à piston axial du type à plateau oscillant, présentant un dispositif de réglage
DE19721036B4 (de) Steuerventil für ein Fahrzeug mit einer Druckmittelanlage
EP1409873B1 (fr) Bloc de distribution pour un dispositif de regulation, en particulier une machine hydrostatique
WO2002077446A1 (fr) Soupape de limitation de pression pour systemes d'injection de carburant
DE1550611A1 (de) Durchflussregelventil
EP1664530B1 (fr) Dispositif de regulation de puissance
EP3039280A1 (fr) Soupape de décharge pour système d'injection de carburant ainsi que système d'injection de carburant
EP1828651B1 (fr) Soupape de limitation de pression presentant une surface differentielle reduite
EP1853824A1 (fr) Dispositif et procede pour une alimentation en lubrifiant
DE10353842A1 (de) Proportional-Magnetventil
DE102009005768B4 (de) Druckregelung einer hydraulischen Antriebseinheit
EP1502027B1 (fr) Dispositif de regulation comprenant une soupape de regulation de valeur limite
EP4060210A1 (fr) Clapet anti-retour
DE3303492C2 (fr)
DE10261634B4 (de) Kombinationsverschraubung für eine Vorrichtung zur Regelung des Flusses von Druckflüssigkeit in einer Durchfluss-Kontrolleinrichtung
DE102009060188B4 (de) Verstellventil für die Verstellung des Fördervolumens einer Verdrängerpumpe mit Kaltstartfunktion
DE102022210469A1 (de) Druckbegrenzungsventilanordnung, modulare Druckbegrenzungsventilanordnung und hydraulische Steueranordnung mit einer derartigen Druckbegrenzungsventilanordnung
EP1694965B1 (fr) Dispositif de regulation de puissance totale
DE3126794C2 (de) Verstellpumpe
DE10035631C2 (de) Nullastschaltung
DE2424272C2 (de) Hubventil
DE102021124684A1 (de) Axialkolbenmaschine mit Steuerventil zur Einstellung des Schrägwinkels der Schrägscheibe
DE10033739A1 (de) Hydrostatisches Getriebe
WO2025146295A1 (fr) Soupape de réservoir pour réservoir de gaz combustible et réservoir de gaz combustible
AT524517A1 (de) Längenverstellbare Pleuelstange mit verbessertem Zylinderdeckel

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20050422

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT SE

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

DAX Request for extension of the european patent (deleted)
RBV Designated contracting states (corrected)

Designated state(s): DE FR GB IT SE

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

RIN1 Information on inventor provided before grant (corrected)

Inventor name: KAUSS, WOLFGANG

Inventor name: LUDESCHER, HARALD

Inventor name: BLUM, KARL-HEINZ

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20071003

REF Corresponds to:

Ref document number: 502004005162

Country of ref document: DE

Date of ref document: 20071115

Kind code of ref document: P

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20080704

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20120823

Year of fee payment: 9

Ref country code: GB

Payment date: 20120823

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20120824

Year of fee payment: 9

Ref country code: FR

Payment date: 20120831

Year of fee payment: 9

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20130830

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130831

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20140430

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130830

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130830

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20130902

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20151022

Year of fee payment: 12

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502004005162

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20170301