EP2711560A1 - Entraînement hydraulique et outil pouvant être actionné hydrauliquement - Google Patents

Entraînement hydraulique et outil pouvant être actionné hydrauliquement Download PDF

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Publication number
EP2711560A1
EP2711560A1 EP12185472.3A EP12185472A EP2711560A1 EP 2711560 A1 EP2711560 A1 EP 2711560A1 EP 12185472 A EP12185472 A EP 12185472A EP 2711560 A1 EP2711560 A1 EP 2711560A1
Authority
EP
European Patent Office
Prior art keywords
pressure
hydraulic
pressure source
switching valve
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
EP12185472.3A
Other languages
German (de)
English (en)
Other versions
EP2711560B1 (fr
Inventor
Engelbert Zwingler
Georg Aneder
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.)
Hawe Hydraulik SE
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Hawe Hydraulik SE
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 Hawe Hydraulik SE filed Critical Hawe Hydraulik SE
Priority to EP12185472.3A priority Critical patent/EP2711560B1/fr
Priority to US13/845,583 priority patent/US9360028B2/en
Publication of EP2711560A1 publication Critical patent/EP2711560A1/fr
Application granted granted Critical
Publication of EP2711560B1 publication Critical patent/EP2711560B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/20—Other details, e.g. assembly with regulating devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F15B11/0423—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling pump output or bypass, other than to maintain constant speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line

Definitions

  • the invention relates to a hydraulic drive according to the preamble of patent claim 1 and a hydraulically actuable tool according to the preamble of claim 13.
  • a known hydraulic drive In a usable, for example, as a cable shoe press, portable, hydraulically actuated tool (with battery or power cord) a known hydraulic drive is used, the switching valve with worker pressure limiting function (the latter by an integrated pressure relief valve) in one of a working line from the pressure source to the hydraulic consumer branching discharge channel is arranged to the tank.
  • the working force is limited by opening the pressure relief valve via the pressure limiting function when a working position is reached.
  • the pressure limiting valve then remains in its open position, so that after switching off the pressure source, the permanently acting force (either a spring or a load) moves the hydraulic consumer over its return stroke to a predetermined end position and thereby the pressure medium from the loading space on the located in the passage position Switching valve can flow to the tank. Then the pressure relief valve returns to the starting position.
  • the switching valve requires, as it also controls the pressure limiting function, high spring force and a relatively narrow throttle point, which causes on the one hand at least a very large pressure application area and on the other hand, a relatively limited sudhub york. The hydraulic consumer always moves back to the end position over the entire return stroke, even if the pressure source is switched on again during the return stroke.
  • the invention has for its object to provide a hydraulic control of the type mentioned above and a hydraulically actuated tool in which energy-saving and without additional equipment components after a work cycle, the time for the complete return stroke of the water consumer needs to be awaited until the end position.
  • the pressure source is a pump which can be operated electrically in the switch-off mode (battery operation or mains cable operation), and the pressure or volume flow impulse necessary for the hydraulic stopping of the return stroke can be generated by at least temporarily switching on the initially switched-off pump. This can be done conveniently for the user via the already existing power switch of the pump.
  • the switching valve and its working pressure-limiting function in a running from the pressure source via the hydraulic consumer and the throttle point to the tank working line connected in parallel, and the working line is passed both to the hydraulic consumer and from the hydraulic consumer to the tank respectively through the switching valve.
  • the working line between the pressure source and the hydraulic consumer is equipped with a from the delivery pressure or flow of the pressure source, a predetermined pressure difference generating control throttle arrangement, either a control throttle and a blocking in the return flow to the pressure source check valve or only in the return flow to the pressure source blocking, includes spring-loaded check valve with control throttle function.
  • the spring force of the switching valve acts in the direction of adjustment to the passage position, while the switching valve in the direction of the shut-off from the upstream of the control throttle arrangement and in the direction of the passage position is additionally pressure-controlled in each case from downstream of the control throttle arrangement.
  • the switching valve for the shut-off position between the hydraulic consumer and the tank has a seat and a seat valve closing member with a sealing surface, preferably between the throttle point arranged at the beginning of the switching valve and a tank connection.
  • the seat valve closing member locks under supply pressure or flow of the pressure source to the seat and is lifted from the seat, without delivery pressure or flow from the spring force of the changeover valve, when the manual override is used or a pressure control. Then the pressure in the chamber breaks down. If this is not the case, the seat valve closing member remains due to the pressure due to the force permanently acting in the hydraulic consumer force on the seat. The changes of the changeover valve take place without loss of time quickly.
  • a communicating with the pressure source Through hole one of the spring force of the changeover valve loaded piston with a cooperating with the through hole closing extension, and, preferably, provided an adjustable abutment for a spring force generating spring.
  • the abutment can either be arranged in the seat valve closing member, for example screwed, and be guided in the housing with the sealed to the outside of the housing seat valve closing member, or the abutment is arranged in the housing separately from the seat valve closing member, for example screwed, the seat valve closing member sealed in the housing encapsulated.
  • a projection extends from the piston sealed by the abutment outwardly from the housing, which lies on the outside of the housing end forms a manual override.
  • a chamber with a pressure source connection is arranged below the seat valve closing member in the housing, which is partially limited away from the seat valve closing member by a chamber bottom.
  • the chamber floor can be designed as an inserted into the housing insert or be an integral part of the housing.
  • the chamber bottom is penetrated by a leading to a hydraulic consumer connection of the housing passage. In the passage is z. B. the control throttle arrangement arranged. This results in short and low-loss flow paths and a compact design of the switching valve.
  • control throttle designed as a EinschraubdrosselURI and designed as a platelet check valve check valve
  • the EinschraubdrosselURI can be conveniently replaced with a trained with other throttle cross-section.
  • the platelet check valve saves space in the axial direction.
  • the spring-loaded check valve with control throttle function can be directly mounted in the passage.
  • the piston for the pressure limiting function can be performed inside in designed as a pot piston with mecanicumflindmaschine conical sealing surface seat valve closing member, and the seat valve closing member inside a sleeve inserted into the housing of the housing are slidably guided ,
  • a pump on and off switch may be provided which, preferably, is operatively associated with either a timer or a program section to turn on the pump to stop the return stroke of the hydraulic consumer over a predetermined period of time, ensuring that the pressure or volume flow impulse is sufficient to switch over the switching valve via a corresponding pressure difference at the control throttle arrangement from the passage position to the shut-off position and to keep it in the shut-off position.
  • Fig. 1 shows a hydraulic drive H, which, but not limited to, for example, incorporated in a hydraulically actuable tool W and shown in a pressureless state.
  • the tool W may be a portable tool, for example for pressing cable lugs, a cutting tool such as an accident scissor, or a turning tool, for example for use in the field and has a suitably replaceable tool insert 1, which is controlled by a hydraulic consumer 2, in the illustrated embodiment of a hydraulically movable hydraulic cylinder with a piston 3 against a permanent force (spring 4 or a load 5).
  • a pressure source P is provided at a tank T, which is operable via an electric motor M in the shutdown mode.
  • This may be a fixed displacement pump with one or more pump elements.
  • the electric motor M is connected to an on-off switch 6, which can be actuated on the tool as needed.
  • the on-off switch 6 is associated with a timer or program section 7 which, with only a brief activation of the on-off switch 6, ensures a predetermined switch-on period, which will be explained later.
  • From the pressure source P performs a working line 9 via a blocking in the return flow to the pressure source P check valve 8 to the hydraulic consumer 2, namely a branch 9a of the working line 9 by a switching valve U with worker pressure limiting function to a Beauftschungsraum 40 of the hydraulic consumer 2, and a branch 9b from the admission chamber 40 through the switching valve U to the tank.
  • the switching valve U has a housing 10, in the in Fig. 1 shown embodiment in block form or as Einschraubpatrone, z. B. steel, which has a pressure source port 11, a hydraulic consumer port 12, a further hydraulic consumer port 13 and a tank port 14 with a specific connection pattern.
  • a communicating with the pressure source port 11 chamber 15 is formed, which is bounded by a chamber bottom 16, a screwed into the housing 10 bushing 17 and designed as a pot piston seat valve closing member 18.
  • the chamber bottom 16 is optionally formed as an insert (as shown), but may also be formed integrally with the housing 10.
  • the bushing 17 guides the seat valve member 18 in a cylindrical guide region 20 and has a seat 19 designed as a circumferential edge for an outer conical sealing surface 21 of the seat valve closing member 18, which is located between the second hydraulic consumer connection 13 and the tank connection 14.
  • the seat valve member 18 is acted upon by a relatively weak spring 22 with spring force in the lifting direction of the seat 19.
  • the spring 22 may optionally be omitted.
  • a piston 23 is slidably provided, which is provided for the worker pressure limiting function of the changeover valve U and the underside carries a closure member extension 24 which cooperates with a passage 29 in the bottom of the poppet valve member 18 (pressure relief poppet valve function).
  • the chamber bottom 16 includes a passage to the first hydraulic consumer port 12.
  • a control throttle assembly A is arranged, which in the embodiment in Fig. 1 consists of a screwed throttle insert 26 with a control throttle 27 of a predetermined cross-sectional size and also in the return flow to the pressure source port 11 locking check valve 28, which is formed in the illustrated embodiment as an axially small plate-check valve.
  • a spring 30 is arranged, which generates the spring force to hold the pressure limiting valve 24, 29.
  • the spring 30 is supported at its other end on an abutment 31, which in the embodiment in Fig. 1 is screwed into the seat valve member 18 and allows a change in the spring force.
  • the piston 23 has a central extension 32, which extends sealed by the spring abutment 31 to the outside of the housing 10 and forms a manual override 33 outside the housing.
  • the seat valve member 18 extends through a seal 34 in the sleeve 17 to the outside of the housing, where structures 36 may be formed, which allow for screwing the abutment 31 Dreridstützung.
  • the embodiment of the hydraulic drive H in Fig. 2 is different from that of Fig. 1 in that, with the same connection pattern of the housing 10a, the abutment 31a is screwed into the bushing 17a and is structurally separated from the piston 23.
  • the seat valve closing member 18a is shorter than in FIG Fig. 1 , It is only the spring 30 is provided while the spring 22 of Fig. 1 is omitted, so that only the spring 30 with the pressure relief valve closed and the seat valve closing member 18 a applied away from the seat.
  • the chamber bottom 16a has opposite Fig. 1 a space-saving modified cross-section.
  • the below-explained function of the hydraulic drive is in both embodiments of the Fig. 1 and 2 identical.
  • control throttle arrangement A can only be replaced by a (not shown) in the return flow to the pressure source port 11 locking spring-loaded check valve with control throttle function in the passage 25.
  • control throttle assembly A could be placed elsewhere in the housing 10, 10a or directly in the hydraulic consumer port 12.
  • Fig. 3 is the switching valve U with its dash-dotted lines indicated housing 10, 10a shown that the switching valve function (components 19, 20, 21) and the pressure limiting function (Components 23, 24, 28), as well as the respective spring force 22, 30 are shown separately, such that in the branches 9a, 9b of the working line 9, the switching valve function and the pressure limiting function are connected in parallel.
  • pilot lines 18 and 39 are indicated by dashed lines in the Fig. 1 and 2 formed on the one hand by the chamber 15 and on the other hand by the throttle body 37.
  • the pilot control line 38 leads from the upstream of the control throttle arrangement A to the closing control side of the seat valve closing member 18, while the pilot control line 39 extends from the downstream of the control throttle arrangement A to the opening control side of the seat valve closing member 18.
  • the commissioning takes place, that is, the pressure source P is turned on.
  • the resulting from the delivery pressure or flow of the pressure source P back pressure generated at the control throttle 27, a pressure difference between the pilot lines 38, 39, whereby the seat valve closing member 18 goes into its shut-off, that is, with the sealing surface 21 tight against the seat 19 tight ,
  • the throttle point 37 is thereby separated from the tank connection 14 (shut-off position).
  • the piston 23 holds closed with the spring force 30 via the closing extension 24, the passage 29, so that the connecting channel 35 is shut off from the tank.
  • the hydraulic consumer 2 moves out.
  • the pressure source is switched off again before reaching the maximum working pressure desired by the pressure limiting function, then it stops due to the permanent force 4; 5 constructed pressure in the admission chamber 40, the switching valve in the shut-off position.
  • the hydraulic consumer remains in the current position. If the manual override 33 is used in this phase of operation, then the resulting pressure is reduced via the connecting channel 35 in the seat valve closing member 18 to the tank and takes the switching valve U via the pressure pilot control from the pilot line 39 his (not shown) passage position, whereupon the hydraulic consumer 2 under the permanently acting force 4; 5 performs a return stroke to the end position.
  • Fig. 4 illustrates the working phase of the hydraulic drive H.
  • the hydraulic consumer 2 is extended to a working position.
  • the pressure source P generates the necessary working pressure.
  • the pressure relief valve With its components 23, 24, 29 controlled against the spring force 30.
  • the pressure relief valve remains open until the pressure in the chamber 15 has dropped so far that the changeover valve U switches. Then the pressure relief valve closes again.
  • Fig. 5 illustrates the decommissioning of the hydraulic drive H by switching off the pressure source P. Since then only the pressure in the loading space 40, caused by the permanent force 4; 5, via the pilot control line 39 and the spring 22 (or a part of the spring force the spring 30) the seat valve closing member 18, as shown, lifted in the passage position from the seat 19 and the hydraulic consumer 2 performs its return stroke to its predetermined end position, with a speed which is optionally predetermined by the bore 37. If it is desired to stop the hydraulic consumer 2 during the return stroke at any point, that is to stop the return stroke is still during the return stroke in Fig.
  • the pressure source P is turned on again until at the control throttle 27 by means of a pressure and / or flow rate pulse back pressure arises, which brings the poppet valve member 18 (arrow 42) back into its shut-off position. If the pressure source for the period mentioned above only temporarily turned on, and then turned off again, then the hydraulic consumer stops at the stopped position. On the other hand, if the pressure source P remains switched on, the hydraulic consumer 2 returns to a working position in which the maximum pressure possibly acts, the seat valve closing member 18 keeping its shut-off position.
  • the hydraulic consumer 2 carries out its complete return stroke, which can be stopped again at any time by renewed switching on of the pressure source.
  • Fig. 1 When the pressure source P (of the electric motor M) is switched on, a pressure difference is generated from the volume flow at the control throttle 27, while the pressurization chamber 40 is pressurized, so that the seat valve closing member 18 moves with its sealing surface 21 against the seat 19 and assumes the shut-off position. As a result, the branch 9b is shut off and the hydraulic consumer 2 moves out.
  • the closing extension 24 keeps the passage 29 shut off; the piston 23 leads into Fig. 1 together with the abutment 31, the movement of the seat valve closing member 18 with.
  • the closing extension 24 lifts off from the passage 29 and pressure medium flows out of the chamber 15 through the passage 29 and the connecting channel 35 to the tank connection 14, the check valve 28 possibly being shut off.
  • the piston 23 moves relative to the seat valve closing member 18 briefly upward against the spring force 30.
  • the connection from the throttle point 37 to the tank port 14 is shut off.
  • the pressure source P is turned off (the electric motor M)
  • the pressure difference across the control throttle 27 decreases, and the seat valve closing member 18 together with the piston 23 at least by the spring force 30 and acting on the throttle 37 pressure in the loading chamber 40 in in the Fig. 1 shown shifted position and lifted off the seat 19.
  • the hydraulic consumer 2 (hydraulic cylinder, hydraulic motor) is optionally arranged in an easily interchangeable manner, ie. H.
  • the hydraulic consumer connections in the housing 10, 10a of the switching valve U form interfaces for combination with different types of hydraulic consumers 2.
  • the switching valve U can be changed, for example, by replacing the throttle insert 26 and / or adjustment of the abutment 31 to change the spring force 30 (22) Vote requirements.
  • the changeover valve U is explained with a block-shaped housing 10, 10a, but could alternatively be a valve cartridge or a screw-in valve.
  • the check valve 28 could be located in the system at a position other than shown.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
EP12185472.3A 2012-09-21 2012-09-21 Entraînement hydraulique pour un outil pouvant être actionné hydrauliquement Not-in-force EP2711560B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP12185472.3A EP2711560B1 (fr) 2012-09-21 2012-09-21 Entraînement hydraulique pour un outil pouvant être actionné hydrauliquement
US13/845,583 US9360028B2 (en) 2012-09-21 2013-03-18 Hydraulic drive and hydraulically operable working tool

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP12185472.3A EP2711560B1 (fr) 2012-09-21 2012-09-21 Entraînement hydraulique pour un outil pouvant être actionné hydrauliquement

Publications (2)

Publication Number Publication Date
EP2711560A1 true EP2711560A1 (fr) 2014-03-26
EP2711560B1 EP2711560B1 (fr) 2019-06-12

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EP12185472.3A Not-in-force EP2711560B1 (fr) 2012-09-21 2012-09-21 Entraînement hydraulique pour un outil pouvant être actionné hydrauliquement

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US (1) US9360028B2 (fr)
EP (1) EP2711560B1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3078456A1 (fr) * 2015-04-10 2016-10-12 HAWE Hydraulik SE Entraînement hydraulique et soupape d'inversion
WO2019121416A1 (fr) * 2017-12-21 2019-06-27 Moog Gmbh Actionneur à amplificateur d'évacuation hydraulique

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2835540B1 (fr) * 2013-08-08 2016-04-27 HAWE Hydraulik SE Entraînement hydraulique
US9862137B2 (en) 2015-04-20 2018-01-09 Milwaukee Electric Tool Corporation PEX expanding tool
WO2016201196A1 (fr) 2015-06-10 2016-12-15 Milwaukee Electric Tool Corporation Outil d'expansion pex
DE102015119108A1 (de) * 2015-11-06 2017-05-11 Pleiger Maschinenbau Gmbh & Co. Kg Verfahren und Vorrichtung zum Ansteuern einer hydraulisch betätigten Antriebseinheit einer Armatur
CN108787192B (zh) * 2017-05-02 2020-07-17 苏州众慧合智能制造有限公司 自激脉冲式节能阀
CN111237288B (zh) * 2020-03-12 2022-03-04 长沙普惠环保机械有限公司 一种垃圾压缩机用多油缸协作压缩补偿系统

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US20110088797A1 (en) * 2009-10-20 2011-04-21 Kayaba Industry Co., Ltd. Fluid-pressure actuator unit

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US5076140A (en) * 1989-03-10 1991-12-31 Pacific Fluid Systems, Corp. Method and system for hydraulically positioning and impact load cushioning of a workpiece
DE10039936A1 (de) * 2000-08-16 2002-03-07 Fluidtech Gmbh Ventil
AT6575U1 (de) * 2002-10-31 2003-12-29 Magna Steyr Powertrain Ag & Co Einfachwirkender aktuator mit schnellöffnendem hydraulikventil zur steuerung einer kupplung
DE102007027603A1 (de) * 2007-06-12 2008-12-18 Voith Patent Gmbh Hydraulischer Antrieb, insbesondere für Werkzeugmaschinen, und Verfahren zum Steuern des hydraulischen Antriebs
SE534002C2 (sv) * 2009-06-24 2011-03-29 Nordhydraulic Ab Förfarande och anordning för styrning av ett hydraliskt system

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US20110088797A1 (en) * 2009-10-20 2011-04-21 Kayaba Industry Co., Ltd. Fluid-pressure actuator unit

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3078456A1 (fr) * 2015-04-10 2016-10-12 HAWE Hydraulik SE Entraînement hydraulique et soupape d'inversion
WO2019121416A1 (fr) * 2017-12-21 2019-06-27 Moog Gmbh Actionneur à amplificateur d'évacuation hydraulique
CN111566357A (zh) * 2017-12-21 2020-08-21 穆格股份有限公司 带液压排流增益器的执行驱动装置
CN111566357B (zh) * 2017-12-21 2022-06-17 穆格股份有限公司 带液压排流增益器的执行驱动装置

Also Published As

Publication number Publication date
US20140083085A1 (en) 2014-03-27
US9360028B2 (en) 2016-06-07
EP2711560B1 (fr) 2019-06-12

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