EP1084349B1 - Dispositif de reglage destine a des appareils hydrauliques - Google Patents

Dispositif de reglage destine a des appareils hydrauliques Download PDF

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Publication number
EP1084349B1
EP1084349B1 EP99924562A EP99924562A EP1084349B1 EP 1084349 B1 EP1084349 B1 EP 1084349B1 EP 99924562 A EP99924562 A EP 99924562A EP 99924562 A EP99924562 A EP 99924562A EP 1084349 B1 EP1084349 B1 EP 1084349B1
Authority
EP
European Patent Office
Prior art keywords
valve
regulating device
control
valve body
flow
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.)
Expired - Lifetime
Application number
EP99924562A
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German (de)
English (en)
Other versions
EP1084349A2 (fr
Inventor
Johann Schmollngruber
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.)
Weber Hydraulik GmbH Austria
Original Assignee
Weber Hydraulik GmbH Austria
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 Weber Hydraulik GmbH Austria filed Critical Weber Hydraulik GmbH Austria
Publication of EP1084349A2 publication Critical patent/EP1084349A2/fr
Application granted granted Critical
Publication of EP1084349B1 publication Critical patent/EP1084349B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • EFIXED CONSTRUCTIONS
    • E21EARTH OR ROCK DRILLING; MINING
    • E21FSAFETY DEVICES, TRANSPORT, FILLING-UP, RESCUE, VENTILATION, OR DRAINING IN OR OF MINES OR TUNNELS
    • E21F11/00Rescue devices or other safety devices, e.g. safety chambers or escape ways
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/20Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205Systems with pumps
    • F15B2211/20576Systems with pumps with multiple pumps
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/30Directional control
    • F15B2211/305Directional control characterised by the type of valves
    • F15B2211/3056Assemblies of multiple valves
    • F15B2211/3059Assemblies of multiple valves having multiple valves for multiple output members
    • F15B2211/30595Assemblies of multiple valves having multiple valves for multiple output members with additional valves between the groups of valves for multiple output members
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15BSYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00Circuits for servomotor systems
    • F15B2211/70Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71Multiple output members, e.g. multiple hydraulic motors or cylinders

Definitions

  • the invention relates to a control device, as in the preamble of claim 1 described.
  • DE 195 51 510 A1 describes a device known for fluid association for construction vehicles, in which starting from two one Pumps delivering pressure medium through appropriate control valves and bypass lines several actuators according to the operating conditions with the pressure medium apply evenly and thus the controllability of the working machine should be improved.
  • the device for fluid combination described is based of two pump units to control four double-acting control units designed and requires a variety of in the described embodiment Control and regulating valves and extensive external line routing.
  • the object of the invention is therefore to provide a control device which optional operation of at least two implements with maximum energy use allows.
  • This object of the invention is characterized by the characterizing features in the claim 1 reached.
  • the surprising advantage here is that the arrangement of a control device A flow connection that can be switched as required in the supply circuits is achieved, with which an accumulation of the medium flow one from a two or multi-circuit pump formed pressure generating device and its concentration on one implement using one control valve per supply circuit is possible. This means higher working speeds, which shorten the operating time and significantly accelerate the recovery process. Furthermore is for the mobile use the weight of the supply unit is crucial and after the training according to the invention becomes a compact and few components exhibiting unit reached. Because the performance immediately the working speed of the implements and often the implements in alternating order are in use, existing resources of the supply unit fully used. Furthermore, after the training according to the invention, connecting lines saved the operational safety by avoiding possible Leakages increased and the assembly effort reduced.
  • An embodiment according to claim 7 is also advantageous, which makes it complicated Flow ducts can be easily manufactured into undivided components in terms of production technology are.
  • An advantageous training as finally described in claim 11, enables a compact and reliable unit because it is short and easy to manage Flow and connection channels and bores can be achieved.
  • a hydraulic unit 1 for supplying at least two work tools 2, 3, e.g. Recovery scissors 4, recovery spreader 5, etc., with a pressure medium 6, e.g. Hydraulic oil 7, shown in a schematic representation.
  • a pressure generating device 9 is arranged in a receptacle 8 for the hydraulic oil 7, .
  • the pressure generating device 9 is preferred for the formation of one for each implement 2, 3 independent Supply circuit 10, 11 equipped, this preferably using one each a dual or multi-circuit pump 12 having a common drive motor.
  • the pressure generating device 9 or the dual or multi-circuit pump 12 is in a further preferred training for the optimal supply of tools 2, 3 at least as a two-stage, ie two-pressure stage pump, whereby Piston pumps in particular for the high pressure level usually used and because of the achievable small dimensions and light weight radial piston pumps are particularly suitable for portable units.
  • the power tool 2 and / or is via flow channels 13 or supply lines 14 the implement 3 with the interposition of a control device 15 with the Hydraulic unit 1 connected.
  • Each of the tools 2, 3 is also with one and one Shut-off valve 16, 17 provided to this even with longer supply lines 14 operating independently of the actuation of the control device 15 or to put out of operation.
  • the control device 15 is in the embodiment shown by a block Valve housing 18 shown in the spaced apart in each of the supply circuits 10, 11 flow-integrated into the flow channels 13 each Valve body 19, 20 is arranged.
  • Receptacles 21 arranged in the valve housing 18, 22 form with the valve bodies 19, 20 control valves 23, 24 used therein Tools 2, 3, which are connected via connecting channels 25 in the valve housing 18 are and with corresponding switching positions of the control valves 23, 24 a flow connection cause between the supply circuits 10, 11.
  • the control valves 23, 24 are preferably designed as rotary slide valves, in which the valve bodies 19, 20 have a cylindrical cross section and by pivoting enable a required number of switch positions.
  • three switching positions per control valve 23, 24 are sufficient, thereby creating operating conditions by means of the control device 15 are switchable, in which each in a first switching position of the control valves 23, 24 of the working devices 2, 3 supplied by one of the independent supply circuits 10, 11 is and in a second switching position, the delivery rate of the dual or multi-circuit pump 12 via a connecting line 25 to one of the supply circuits 10, 11 and for the supply of only one of the tools 2, 3 is concentrated in order to achieve higher working speeds or in a third switching position, in which the promotion of the pressure medium 6 in the direction of the tools 2, 3 prevented is, the pressure medium delivered by the dual or multi-circuit pump 12 returned directly into the receptacle 8 via the control valves 23, 24 becomes.
  • FIG. 2 the hydraulic unit 1 with the pressure generating device 9 and the Control device 15 shown.
  • the pressure generating device 9 is shown in FIG Embodiment a two-circuit radial piston pump 26 on a one or more parts formed plate-shaped housing part 27, which is driven by a drive shaft 28 a drive motor 29 which e.g. is flanged to the housing part 27, is penetrated and is attached to the pump elements 30.
  • the pump elements 30 are standard delivery elements for the pressure medium 6 and are self-priming. In the embodiment shown are on the housing part 27 six pieces of the pump elements 30 attached. Of which are each three pieces via flow channels arranged in two levels in the housing part 27 31 connected to the supply circuits 10, 11. To form a multi-level Execution of the pressure generating device 9 becomes each of the supply circuits 10, 11 supplied by two high pressure elements 32 and a low pressure element 33.
  • the pump elements 30 are acted upon by a drive shaft 28 non-rotatably coupled eccentric element 34 which on the drive shaft 28 in this axial direction is adjustable and by changing the eccentricity at such Adjustment of the delivery rate between a zero value and a maximum value is adjustable.
  • the pump elements 30 including those through the drive shaft 28 and the eccentric element 34 formed drive assembly 35 are surrounded by hydraulic oil 7, the itself in the receptacle 8 which is flanged on the housing part 27 in a liquid-tight manner is located with the usual facilities for such a receptacle 8 such as filler cap, drain cap and level indicator.
  • the passage of the drive shaft 28 through the housing part 27 is after State of the art liquid-tight.
  • the housing part 27 is e.g. Damping elements 36 forming via feet in one Support frame 37 formed from tubes mounted.
  • valve body 19, 20 in the position shown are activated, each of the supply circuits 10, 11 a pressure line 39 and has a return line 40, which is formed from hydraulic hoses and screw connections are connected to the valve housing 18.
  • the flow channels 13 in Valve housing 18 and the valve bodies 19, 20 allow in the position shown the inflow of the print medium from the pressure generating device 9 independently from each other to each of the supply circuits 10, 11 and the return of the print medium 6 in the receptacle 8 via flow channels 13 and outlet openings 41 in the housing part 27.
  • the connecting line is 14 deactivated.
  • Fig. 3 the control device 15 with the control valves 23, 24 is shown.
  • the Control valve 23 is in the supply circuit 10 and the control valve 24 in the supply circuit 11 arranged.
  • In an end face 42 of the valve housing 18 are spaced apart the receptacles 21, 22 for the valve body 19, 20 through cylindrical bores 43 arranged.
  • the valve body 19 of the control valve 23 is cylindrical and a diameter 44 of the bore 43 adapted so that a tilt-free Swiveling the valve body 19 in the bore 43 is possible.
  • a height of 45 Valve body 19 is smaller than a depth 46 of bore 43.
  • a cylindrical extension 48 Coaxial to a central axis 47 is integrally connected to the valve body 19, a cylindrical extension 48 arranged, which has a diameter 49 which is approximately half as large as the diameter 44.
  • the extension 48 extends from the cylinder body 19 in the direction the end face 42 of the valve housing 18 and projects beyond it. Including the extension 48 is on the end face 42 with an annular flange an annular, in the receptacle 21 protruding sealing body 50 attached. Sealing elements 51 ensure a Sealing between the sealing body 50 and the valve housing 18 and the Sealing body 50 and the extension 48.
  • valve body 19 In the valve body 19 are in the opposite of the extension 48 and a base 55 the end face 56 facing the receptacle 56 inlet and outlet openings 57 arranged in the valve body 19 bores 58. These inflow and outflow openings 57 are depending on the position of the valve body 19 in the valve housing Assigned 18 provided flow channels 31. Via the flow channels 31 and Boreholes 58 become this according to an arrow 59 from the pressure generating device 9 supplied pressure medium 6 of the pressure line 39 and thus the supply circuit 10 fed and returned via the return line 40.
  • the control valves 23, 24 are also connected to one another via the connecting channel 25 a preselectable switching position fluidly connected, with such Switch position either one of the supply circuits 10, 11 is blocked and thus the total oil flow of the two- or multi-circuit pump 12 one of the supply circuits 10, 11 and thus tools 2, 3 is supplied, thereby reducing the working speed of the working device 2, 3 which is acted upon in a concentrated manner in such a case is proportional to the delivered volume of the pressure medium 6 is increased.
  • both supply circuits 10 are independent of one another. 11 activated and an independent use of the tools 2, 3 is possible.
  • control device 15 consisting of the control valves 23, 24 for the different operating conditions, based on the usual in hydraulics Symbolism shown.
  • valve bodies 19, 20 are provided in a circular cross section Bores 58 as a settlement for positions 61, 62, 63 for the control valve 23 and shown for positions 64, 65, 66 for the control valve 24.
  • the control valve 23 is now in the switch position 63 and the control valve 24, as already described in FIG. 4, in the switching position 64, the medium flow delivered from the dual-circuit radial piston pump 26 in the valve body 19 via a bypass channel 68 past the check valve 60 and supplied via the connecting channel 25 to the control valve 24 and additionally the medium flow flowing in the direction of the supply circuit 11 against the blocking effect of the check valve 60 in the valve body 20 fed to the implement. So that flows in the supply circuit 11, the entire delivered by the dual-circuit radial piston pump 26 Volume, resulting in an increase in working speed for the implement leads.
  • Control valve 23 is in the switching position 61 already described in FIG. 4 and that Control valve 24 is in the switching position 66, which also means that in the valve body 20 provided bypass channel 68 for the check valve 60 to effect comes and the control valve 24 supplied flow through the connecting channel 25 flows to the control valve 23, whereby the entire in the supply circuit 10 subsidized electricity comes into effect.
  • control valves 23, 24, designed as rotary slide valves, are of course also training as spool valves - so with linearly movable control piston - possible.
  • Such an implementation however a higher effort in the manufacture of the control piston of the valve housing and in terms of sealing and also requires more space and weight connected.
  • the tools 2, 3 are usually already with integrated switching valves, which fulfill a switch-on and switch-off function, since these usually are connected to the hydraulic unit 1 via longer hose lines, so to be able to switch tools 2, 3 on and off immediately at the place of use.
  • control device 15 instead of the manually operated version to be equipped with remotely controllable actuators in order to switch over the Control device 15 to the individual switching positions from any location to be able to perform.
  • control device 15 For the sake of order, it should finally be pointed out that for better understanding of the structure of the control device 15 this or its components are sometimes not to scale and / or enlarged and / or reduced.
  • FIGS. 1, 2; 3; 4 to 6 shown versions form the subject of independent solutions according to the invention.
  • the related, Tasks and solutions according to the invention are the detailed descriptions these figures.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid Mechanics (AREA)
  • Mining & Mineral Resources (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Geochemistry & Mineralogy (AREA)
  • Geology (AREA)
  • Business, Economics & Management (AREA)
  • Pulmonology (AREA)
  • Emergency Management (AREA)
  • Health & Medical Sciences (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un dispositif de réglage destiné à au moins deux appareils de travail (2, 3), par exemple, une cisaille minière (4) ou une poutrelle minière (7), qui sont actionnés par un agent de pression (6) notamment une huile hydraulique (7) et qui sont respectivement dotés d'un outil (2, 3), d'un circuit d'alimentation (10, 11) destiné à l'agent de pression (6) et d'au moins un dispositif de production de pression (9). Les circuits d'alimentation (10, 11) de ces appareils (2, 3) renferment respectivement un dispositif de commande (15) constitué d'une valve de commande (23, 24) et les valves de commande (23, 24) sont, si besoin, en communication fluidique par au moins un canal de liaison (25) ou une conduite de liaison.

Claims (11)

  1. Dispositif de réglage pour au moins deux appareils de travail (2, 3) actionnés par un milieu sous pression (6),notamment par de l'huile hydraulique, par exemple une cisaille de remblais (4), un écarteur de remblais (5), etc, avec un circuit d'alimentation (10, 11) pour le milieu sous pression (6) pour chaque appareil de travail (2, 3) et avec au moins un dispositif générateur de pression (9) et avec un dispositif de commande (15) formé dans les circuits d'alimentation (10, 11) pour les appareils de travail (2, 3) par des vannes de commande (23, 24) où les vannes de commande (23, 24), sont en liaison d'écoulement selon le besoin par au moins un canal de liaison (25) ou une ligne de liaison, et où deux vannes de commande (23, 24) sont disposées dans un boítier de vannes commun (18) présentant le canal de liaison (25), caractérisé en ce qu'il est disposé par circuit d'alimentation (10, 11) pour les appareils de travail (2, 3) une vanne de commande (23, 24), et que chaque vanne de commande (23, 24) présente trois positions de commutation, où dans une première position de commutation des vannes de commande (23, 24), chacun des appareils de travail (2, 3) est alimenté par l'un des circuits d'alimentation indépendants (10, 11) et où avec une vanne de commande (23, 24) dans la deuxième position de commutation et l'autre vanne de commande (23,24) dans la première position de commutation, le flux de milieu convoyé par le dispositif générateur de pression (9) est amené par le canal de liaison (25) de la vanne de commande dans la deuxième position de commutation à la vanne de commande (23, 24) dans la première position de commutation, et ainsi la puissance de convoyage du dispositif générateur de pression (9) est concentrée sur un appareil de travail (2, 3) et où dans une troisième position de commutation des vannes de commande (23, 24), le convoyage est empêché.
  2. Dispositif de réglage selon la revendication 1, caractérisé en ce que la vanne de commande (23, 24) est réalisée sous forme de vanne à tiroir tournant qui présente un corps de vanne (19, 20) sensiblement cylindrique qui est disposé d'une manière tournante respectivement pivotante dans le boítier de vannes (18) pourvu de canaux d'écoulement (13).
  3. Dispositif de réglage selon la revendication 1, caractérisé en ce que la vanne de commande (23, 24) est réalisée sous forme de vanne à robinet de piston.
  4. Dispositif de réglage selon l'une ou plusieurs des revendications précédentes, caractérisé en ce qu'un boítier de vannes (18) des vannes de commande (23, 24) est fixé sur une face frontale (38) d'une partie de boítier (27) portant le moteur d'entrainement (29) et les éléments de pompe (30).
  5. Dispositif de réglage selon la revendication 2, caractérisé en ce que le corps de vanne (19, 20) présente au moins un perçage (58) qui forme une liaison d'écoulement entre les ouvertures d'afflux et d'écoulement (57).
  6. Dispositif de réglage selon la revendication 5, caractérisé en ce que les ouvertures d'afflux et d'écoulement (57) du perçage (58) sont ménagées dans une face frontale (56) du corps de vanne (19, 20).
  7. Dispositif de réglage selon la revendication 1, caractérisé en ce que des canaux d'écoulement (31) sont disposés dans le boítier de vanne (18) ou dans une partie de boítier (27) dans au moins deux plans parallèles et s'étendant parallèlement à un axe médian du corps de vanne (19, 20).
  8. Dispositif de réglage selon la revendication 5 ou 6, caractérisé en ce que sont disposés dans le corps de vanne (19, 20), le cas échéant, dans des perçages (58) entre les ouvertures d'afflux et d'écoulement (57) des clapets de non-retour (60) chargés par ressort.
  9. Dispositif de réglage selon la revendication 8, caractérisé en ce que le canal de liaison (25) du corps de vanne (19, 20) forme avec des perçages (58) s'étendant dans le boítier de vannes (18), formant deux entrées et deux sorties, par position de commutation, en cas de besoin, une liaison d'écoulement.
  10. Dispositif de réglage selon la revendication 1, caractérisé en ce que respectivement une ouverture d'écoulement des corps de vanne (19, 20) est en liaison d'écoulement par le canal de liaison (25) dans le boítier de vannes (18) avec respectivement une sortie par circuit d'alimentation (10, 11).
  11. Dispositif de réglage selon la revendication 1, caractérisé en ce que le boítier de vanne (18) du dispositif de commande (15) est fixé sur la partie de boítier (27) du dispositif générateur de pression (9) avec les canaux d'écoulement (13) selon une liaison d'écoulement avec des canaux d'écoulement (31) s'étendant dans la partie de boítier (27) du dispositif générateur de pression (9).
EP99924562A 1998-06-12 1999-06-08 Dispositif de reglage destine a des appareils hydrauliques Expired - Lifetime EP1084349B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
AT39298U 1998-06-12
AT0039298U AT3018U1 (de) 1998-06-12 1998-06-12 Regelvorrichtung für hydraulische arbeitsgeräte
PCT/AT1999/000145 WO1999066212A2 (fr) 1998-06-12 1999-06-08 Dispositif de reglage destine a des appareils hydrauliques

Publications (2)

Publication Number Publication Date
EP1084349A2 EP1084349A2 (fr) 2001-03-21
EP1084349B1 true EP1084349B1 (fr) 2002-11-27

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EP99924562A Expired - Lifetime EP1084349B1 (fr) 1998-06-12 1999-06-08 Dispositif de reglage destine a des appareils hydrauliques

Country Status (6)

Country Link
US (1) US6578357B1 (fr)
EP (1) EP1084349B1 (fr)
AT (2) AT3018U1 (fr)
AU (1) AU4121499A (fr)
DE (1) DE59903552D1 (fr)
WO (1) WO1999066212A2 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010034187A1 (de) 2010-08-12 2012-02-16 Lukas Hydraulik Gmbh Steuereinrichtung für erstes und zweites Arbeitsgerät
US8496449B2 (en) 2006-11-21 2013-07-30 Actuant Corporation Air driven hydraulic pump
AT516181A4 (de) * 2014-10-08 2016-03-15 Weber Hydraulik Gmbh Hydraulikaggregat

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CN104295563B (zh) * 2014-03-25 2016-09-07 张志成 活塞往复式脉冲数字流发生装置
US20160221171A1 (en) * 2015-02-02 2016-08-04 Caterpillar Inc. Hydraulic hammer having dual valve acceleration control system
US11958177B2 (en) 2018-09-07 2024-04-16 Milwaukee Electric Tool Corporation Hydraulic piston pump for a hydraulic tool

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8496449B2 (en) 2006-11-21 2013-07-30 Actuant Corporation Air driven hydraulic pump
DE112007002818B4 (de) * 2006-11-21 2016-03-24 Actuant Corporation LUFTBETRIEBENE HYDRAULIKPUMPE MIT FUßBETÄTIGTEM LUFT- UND HYDRAULIKVENTIL
DE102010034187A1 (de) 2010-08-12 2012-02-16 Lukas Hydraulik Gmbh Steuereinrichtung für erstes und zweites Arbeitsgerät
WO2012019758A1 (fr) 2010-08-12 2012-02-16 Lukas Hydraulik Gmbh & Co. Kg Dispositif de commande pour un premier et un deuxième outil de travail
AT516181A4 (de) * 2014-10-08 2016-03-15 Weber Hydraulik Gmbh Hydraulikaggregat
AT516181B1 (de) * 2014-10-08 2016-03-15 Weber Hydraulik Gmbh Hydraulikaggregat
EP3012463A1 (fr) * 2014-10-08 2016-04-27 Weber-Hydraulik GmbH Agregat hydraulique
US10041508B2 (en) 2014-10-08 2018-08-07 Weber-Hydraulik Gmbh Hydraulic unit

Also Published As

Publication number Publication date
DE59903552D1 (de) 2003-01-09
US6578357B1 (en) 2003-06-17
EP1084349A2 (fr) 2001-03-21
WO1999066212A3 (fr) 2000-04-06
AU4121499A (en) 2000-01-05
WO1999066212A2 (fr) 1999-12-23
AT3018U1 (de) 1999-08-25
ATE228616T1 (de) 2002-12-15

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