EP2448720A1 - Presse hydraulique - Google Patents

Presse hydraulique

Info

Publication number
EP2448720A1
EP2448720A1 EP10727433A EP10727433A EP2448720A1 EP 2448720 A1 EP2448720 A1 EP 2448720A1 EP 10727433 A EP10727433 A EP 10727433A EP 10727433 A EP10727433 A EP 10727433A EP 2448720 A1 EP2448720 A1 EP 2448720A1
Authority
EP
European Patent Office
Prior art keywords
control valve
valve
hydraulic
hydraulic fluid
return
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
EP10727433A
Other languages
German (de)
English (en)
Other versions
EP2448720B1 (fr
Inventor
Egbert Frenken
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.)
Gustav Klauke GmbH
Original Assignee
Gustav Klauke 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=43298832&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP2448720(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Gustav Klauke GmbH filed Critical Gustav Klauke GmbH
Priority to PL10727433T priority Critical patent/PL2448720T3/pl
Publication of EP2448720A1 publication Critical patent/EP2448720A1/fr
Application granted granted Critical
Publication of EP2448720B1 publication Critical patent/EP2448720B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25B—TOOLS OR BENCH DEVICES NOT OTHERWISE PROVIDED FOR, FOR FASTENING, CONNECTING, DISENGAGING, OR HOLDING
    • B25B27/00—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for
    • B25B27/02—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for connecting objects by press fit or detaching same
    • B25B27/10—Hand tools, specially adapted for fitting together or separating parts or objects whether or not involving some deformation, not otherwise provided for for connecting objects by press fit or detaching same inserting fittings into hoses
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D22/00—Shaping without cutting, by stamping, spinning, or deep-drawing
    • B21D22/02—Stamping using rigid devices or tools
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D39/00—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders
    • B21D39/04—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders of tubes with tubes; of tubes with rods
    • B21D39/048—Application of procedures in order to connect objects or parts, e.g. coating with sheet metal otherwise than by plating; Tube expanders of tubes with tubes; of tubes with rods using presses for radially crimping tubular elements
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21J—FORGING; HAMMERING; PRESSING METAL; RIVETING; FORGE FURNACES
    • B21J15/00—Riveting
    • B21J15/10—Riveting machines
    • B21J15/16—Drives for riveting machines; Transmission means therefor
    • B21J15/20—Drives for riveting machines; Transmission means therefor operated by hydraulic or liquid pressure
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B25—HAND TOOLS; PORTABLE POWER-DRIVEN TOOLS; MANIPULATORS
    • B25F—COMBINATION OR MULTI-PURPOSE TOOLS NOT OTHERWISE PROVIDED FOR; DETAILS OR COMPONENTS OF PORTABLE POWER-DRIVEN TOOLS NOT PARTICULARLY RELATED TO THE OPERATIONS PERFORMED AND NOT OTHERWISE PROVIDED FOR
    • B25F5/00—Details or components of portable power-driven tools not particularly related to the operations performed and not otherwise provided for
    • B25F5/005—Hydraulic driving means
    • 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

Definitions

  • the invention relates to a hydraulic pressing device with a fixed part and a moving part, wherein the moving part is moved by a hydraulic piston relative to the fixed part and by means of a return spring in an initial position réellebewegbar, wherein further the return movement in response to a predetermined pressing pressure can be triggered by addressing a Return valve, wherein, in addition, a control valve is provided which, in addition to the return valve in the open state, a hydraulic liqueur drain free and has a hydraulic fluid inflow and outflow side.
  • Such pressing devices are known in various configurations. For example, reference should be made to WO 99/19947.
  • WO 98/24570 relating to an application as a punching device
  • WO 02/62504 relating to an application as a widening tool
  • WO 02/00368 relating to an application as a riveting tool.
  • Such a pressing device is also known for example from DE 20 2004 000 215 Ul.
  • the control valve arranged here in a hydraulic line leading from the hydraulic fluid pump to the hydraulic piston receiving hydraulic cylinder is penetrated by the hydraulic fluid delivered by the pump according to a design as a check valve from the inflow side to the outflow side.
  • the fluid pressure acting on the downstream side together with a biasing spring acting in the same direction, causes the control valve to move to the open position, thereby releasing the hydraulic fluid discharge associated with the downstream side.
  • the control valve does not open at higher system pressure, there is still no opening of the control valve at the beginning of the hydraulic fluid return when the return valve has opened after the pressing operation has taken place.
  • the invention is in one aspect with the task of making such a hydraulic pressing device with regard to the response of the control valve advantageous. Another aspect relates to an advantageous arrangement of the control valve.
  • a possible solution in any case of said first aspect is given by a first inventive concept by the subject-matter of claim 1, wherein it is based on the control valve is acted upon by the pressure of the returning hydraulic fluid on the arrival and downstream side with the return valve open, wherein the Throttling pressure is lower on the upstream side.
  • the control valve With the return valve open, the control valve is exposed to the pressure of the hydraulic medium in the return area, albeit differently, on both sides.
  • the resulting due to the throttling pressure difference acts in the opening direction of the control valve and thus causes or in any case supports a rapid opening. This effect can be additionally supported by a spring bias of the control valve in the open position.
  • a possible solution, in particular the further indicated aspect of the problem, is also given by the subject matter of claim 2, the latter being geared to providing a hydraulic pump, from which pump a (first) hydraulic fluid flow path leads to the control valve and another (second) hydraulic fluid flow path leads directly to the return valve.
  • the hydraulic fluid supply line leading from the hydraulic fluid pump to the control valve and preferably also to a hydraulic cylinder receiving the return piston is also provided directly from the hydraulic fluid pump to the control valve.
  • the said hydraulic fluid flow paths can also partially coincide. It is essential that, due to the direct connection, the hydraulic fluid flows through the supply line to the control valve or to the return valve without initially flowing, for example with respect to the return valve, via the control valve.
  • a parallel circuit is provided starting from the hydraulic fluid pump.
  • Hydraulic fluid inlet (from the pump) and hydraulic fluid drain through the (opened) return valve are located hydraulically on the same side of the control valve.
  • the connection to the cylinder chamber (moving part) is located hydraulically on the other side of the control valve (or in the bypass for this purpose).
  • the return valve Seen from the moving part, the return valve may be arranged hydraulically after the control valve or, at least in addition, in parallel with the control valve.
  • Essential is the possible compact arrangement of said valves and the hydraulic lines.
  • the biasing the control valve in the open position spring can be formed with a relatively low spring force.
  • no opening of the control valve is given even when stopping the pump in the course of the initiation of the compression process or in an already more advanced compression. Rather, the control valve moves only in its open position, if in addition, according to the open return valve, a negative pressure of the control valve or an admission pressure difference sets.
  • the compression is actuated triggering of the pump, which is preferably driven by an electric motor achieved. If the depression of a corresponding switch is interrupted, the pump also stops running. Press jaws of a pressing device remain in a certain position.
  • the resumption of the operation allows the injection process to be continued without further ado. There is no running back of the hydraulic piston. Not even with a very low system pressure or (over) pressure level in the hydraulic cylinder at the beginning of a grouting process.
  • control valve is chosen for a clear conceptual separation.Other characteristics of the invention are described below, also in the description of the figures, often in their preferred assignment to the claim concept already explained above but also in an assignment to only one or more features of this claim or independently or in another overall concept of importance.
  • control valve is designed as a seat valve.
  • the valve By driving against a seat stop, the valve closes the hydraulic fluid drain.
  • the opening closed by the seat valve runs (in relation to an axis of the opening) in the direction of displacement of the control valve. There is no Abschieberung, but a closure of a drain opening whose opening area in coverage of the control valve, based on a projection in the direction of movement of the control valve is located.
  • the closed control valve is affected by one of the pressure in the hydraulic fluid reservoir and the pressure in the hydraulic fluid supply line applied differential force is applied. Since in almost all operating conditions, the pressure in the hydraulic fluid supply line is higher than the pressure in the hydraulic fluid reservoir, this results in a locking force of the control valve when it is in the closed position. Although initially a higher pressure is required to move the control valve in the closed position, then, when it is in the closed position, also a lower pressure in the hydraulic medium supply line, as long as this pressure is still sufficiently higher than that Pressure in the hydraulic fluid reservoir.
  • the pressure in the hydraulic fluid reservoir may correspond to the ambient pressure or may even be lower than the ambient pressure, that is to say a negative pressure.
  • the latter especially if the pump works at high flow rate.
  • the higher pressure which serves to displace the control valve into the closed position results from the pressure loss of the flowing hydraulic fluid via the control valve, seen from the inflow side to the outflow side. It is, as it were, a dynamic pressure due to the movement of the hydraulic fluid or the pressure difference resulting from the control valve.
  • the control valve responds to the direction of flow of the hydraulic fluid. The pressure in the hydraulic medium supply line increases accordingly in the
  • Triggering a pressing operation from ambient pressure (or slightly above) to the pressing triggering pressure can for example be between 300 and 700 bar.
  • a trigger pressure can for example be between 300 and 700 bar.
  • the hydraulic fluid pump delivers via a delivery line into a first branch line leading to the control valve and a second branch line leading to the return valve.
  • the return valve is closed or is closed, for example, by releasing an opening detent in the course of this triggering.
  • the hydraulic fluid is therefore only in this branch line, but does not flow. However, it then flows via the control valve and the hydraulic fluid supply line into the cylinder chamber.
  • a bypass can be provided directly in the cylinder chamber.
  • the promotion to the return valve is carried out according to line or not only via the control valve, but, if appropriate, in parallel thereto.
  • the return valve is hydraulically connected in parallel to the control valve with respect to the hydraulic fluid delivery. Further, it is preferably also provided in this context that when the return valve is opened via the return valve, the hydraulic fluid flowing out initially, preferably as a whole, flows via the control valve. In this case, the return valve is hydraulically connected downstream of the control valve at draining hydraulic fluid. But it can also be provided that it flows only partially through the control valve.
  • the control valve may be biased by a spring in its open position. This bias is preferably chosen to be lower in this case than corresponds to a force acting on the control valve by a spring action of the return piston force.
  • the caused by the spring action of the return piston in the case of the return in the hydraulic medium supply line pressure which, as stated, for example, between 0.5 and 5 bar can, corresponding to the hydraulically effective surface of the control valve to a force acting thereon.
  • the said force exerted by the spring action of the return piston force is greater than that corresponding to the force acting on the control valve in the opening direction spring force.
  • a realistic size for the force of this spring acting on the control valve in the opening direction is, for example, between 0.1 and 1 Newton, more preferably between 0.2 and 0.4 Newton, in which ranges also all intermediate values, in particular in 1 / 10 Newton steps are included.
  • hydraulic fluid at least partially flows via the control valve to the return valve
  • the control valve in its open position at the same time the hydraulic fluid supply line, via which otherwise Hydraulic fluid can flow to the return valve locks.
  • this blocking may preferably also be given in the sense of a seat valve.
  • the outflow can then be provided via an example provided direct line connection from the hydraulic cylinder to the return valve, as already mentioned.
  • the outflow via the return valve can thereby be completely interrupted.
  • the return valve goes in this case, because of the associated pressure drop, immediately in its closed position.
  • the return valve is set to the highest pressure, the pressure to be achieved.
  • the control valve allows due to the (further) pressure drop resulting from its opening an automatic control of the return valve in the closed position, with simultaneous opening of a (further) discharge path for the hydraulic fluid. This can be achieved in the desired manner in the course of carrying out a pressing process first, take each intermediate position and then continue the pressing process. After the Verpressvorganges can be achieved by simply re-actuation of the pump stopping the moving part, so usually the return piston, and made from this position from the next pressing.
  • the control valve consists in detail of a valve closure body, which cooperates with a - fixed to the housing - valve seat.
  • the valve closure body passes through a compensating part that accompanies the movement of the valve closure body.
  • the compensation part thus moves with the valve closure body from the closed position to the open position and vice versa.
  • the compensating part is designed such that the valve closure body can move transversely to its direction of movement when moving from the closed position to the open position or vice versa.
  • the valve closure body is also preferably received in the hydraulic medium supply line with a corresponding play. This mobility of the valve closure body ensures that even with not exactly aligned alignment of the valve seat with the valve closure body results in a reliable closure of the control valve.
  • the valve closure body accordingly has sufficient movement possibility with respect to possible manufacturing tolerances.
  • the compensating part may be formed, for example, in the form of a washer.
  • the compensation part for example, specifically the washer, is preferably not sealing in the further preferred at least in this area cylindrically shaped hydraulic fluid supply line fitted.
  • a realistic size for such a gap is about 1/100 to 2/100 mm.
  • the possibility of movement of the valve closure part transversely to the direction of movement with respect to an ⁇ kanns founded. Closing process be 2/100 to 10/100 or more hundredths of a millimeter, for example, up to a 1/2 mm.
  • Fig. 1 is a partially sectioned, representation of a front
  • FIG. 2 is an enlargement of the range 2-2 in Figure 1, with the control and return valve closed. 3 shows an illustration according to FIG. 2, with the control valve open; FIG.
  • FIG. 4 shows a representation according to FIG. 2 with additional throttle opening
  • 5 shows an illustration according to FIG. 4, with a modified throttle opening
  • Fig. 6 is an enlarged view of the control valve relative to the area VI - VI in Fig. 3, with compensation part. Illustrated and described, first with reference to Fig. 1, a hydraulic pressing device with a fixed part 2 and a moving part 3.
  • the moving part 3 is by means of a hydraulic piston 4 relative to the fixed part 2, which can also be regarded as the entire housing moves ,
  • the hydraulic piston 4 can be moved back into its initial position by means of a restoring spring 5 and, in the non-use state, is thereby biased into the starting position.
  • the return movement of the hydraulic piston 4 can be triggered by the response of a return valve 6 at the end of a pressing operation.
  • this return valve 6 is designed and operates in the manner described in EP 0 944 937 B1.
  • the disclosure of this document is hereby incorporated by reference in its entirety into the disclosure of the present application with regard to the design of this return valve and the corresponding mode of operation, also to include one or more of the features known therein in claims of this application.
  • a control valve 7 which influences the closure characteristic of the return valve 6. Because preferably, the return valve 6 is no longer open until complete return of the hydraulic piston 4. According to the control valve 7 results in the opening state of this control valve 7 such a strong pressure drop before the return valve 6, that it prematurely in this sense, before the hydraulic piston 4 reaches its end-return position closes. A further return movement of the hydraulic piston 4 then takes place only by the outflow of hydraulic fluid via the discharge opening 8 released from the control valve 7 in the opening state into the hydraulic fluid reservoir 9.
  • control valve 7 has an inflow side 10 and an outflow side 11.
  • the inflow side 10 refers to the fact that the control valve 7 is acted upon by the hydraulic medium on this side during the conveyance of hydraulic fluid by means of the hydraulic fluid pump 12.
  • the hydraulic pump 12 may be a piston pump as shown. But it may also be, for example, a screw pump. The latter has the advantage that it is pumped with a continuous pressure.
  • control valve as a shuttle valve
  • the control valve in one position (closed position) closes the drain opening 8 and in the other position (with respect to the final position 8: open position) closes the flow to the return valve 6 results a closing of the return valve 6 even in the event that it should have such a large hysteresis that it would otherwise remain in the open position during the entire return of the hydraulic piston.
  • the design can also be provided so that even in the opening state of the control valve 7 according to FIG. 3, a flow of hydraulic fluid to the return valve 6 remains.
  • the spring 5 relaxes and the pressure exerted on the hydraulic fluid pressure is reduced.
  • the return valve 6 can then also be moved into a closed position, if a required critical pressure, which is necessary to maintain the opening state of the return valve 6, is exceeded.
  • the setting can also be made such that, in order to achieve the fastest possible retraction of the hydraulic piston, the control valve 7, as well as the return valve 6, remain in the open position until reaching the end position.
  • the setting is provided so that the return valve 6 immediately moves into its closed position when the control valve 7 opens.
  • the flow of the hydraulic fluid then takes place only through the drain opening 8, which is formed in the valve seat of the control valve 7.
  • a conveying path 19 provided in the bypass for this purpose, see FIGS. 4, 5, may be formed. This is preferably formed as a throttle point. According to FIG. 5, it can also be closed by a check valve 20 so that hydraulic fluid flows through the delivery path 19 only when pumping hydraulic fluid through the pump 12.
  • hydraulic fluid flows through the delivery path 19 into the space 21 and from there, with the return valve 6 open, via the return valve 6 into the hydraulic fluid reservoir 9.
  • the control valve 7 is immediately moved to the closed position.
  • the return spring 16, which acts on the control valve 7 in the open position in this case is designed so that even after a successful initiation of the pressing operation interrupting the pump, such as by the switch is no longer pressed, acting on the control valve 7 closing pressure is sufficient to keep the control valve 7 in the closed position. Then there is no return of the hydraulic piston 4. By pressing the release switch again then the pressing process can be continued, at the same position of the hydraulic piston 4, this has taken on interruption of the pumping operation.
  • the pump 12 can be actuated again at any time by a switch actuation.
  • the control valve 7 moves in the closed position, whereby the hydraulic piston 4 is stopped at the then reached position in the hydraulic cylinder 14. Without a complete retraction is required, then from this position, the next compression can be performed.
  • the control valve 7 is seen to be formed in further detail with a front cone-shaped seating area 22, which merges via a cylinder portion 23 into an enlarged flange area 24. At the end of this flange region 24, a throttling region 25 adjoins.
  • a baffle 31 is provided on the supply chamber side. Even with a small diameter of the drain opening 8, a thin, strong hydraulic fluid jet caused thereby can not lead to damage of the opposite wall 32 of the storage space 9. Especially since the wall 32 is preferably formed by a resilient rubber material.
  • the baffle 31 is formed in detail by a T-tube, wherein a portion of the T-tube is formed as Einschraubabites, the end forms the seat for the control valve 7 and the other portion of the T-tube forms said baffle.
  • the compensation part 33 is designed as an annular body having an inner diameter Di which is smaller than an outer diameter Da of the flange region 24.
  • the compensating part 33 is seated on the seat area side of the flange region 24, ie in the embodiment of the cylinder section 23, penetrated by the valve closure body.
  • the inner diameter Di of the compensation part 33 leaves a gap s with respect to the said cylinder part 23. This gap s allows the valve closure body to move transversely to its longitudinal extent. This automatically results in a certain transverse displacement when, for example, the counter-valve seat forming bore 34 of the here formed by the T-tube valve seat portion 34 should not be aligned with a longitudinal center axis of the valve body.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Safety Valves (AREA)
  • Check Valves (AREA)
  • Fluid-Driven Valves (AREA)
  • Press Drives And Press Lines (AREA)

Abstract

L'invention concerne une presse hydraulique (1) comprenant un partie fixe (2) et une partie mobile (3), la partie mobile étant déplacée par un piston hydraulique (4) par rapport à la partie fixe (2) et pouvant être reculée au moyen d'un ressort de rappel (5) dans une position de départ, le mouvement de recul pouvant être déclenché également en fonction d'une pression d'application prédéfinie par l'actionnement d'un clapet anti-retour (6), une soupape de commande (7) étant prévue d'autre part, laquelle libère un écoulement d'agent hydraulique (8) en supplément du clapet anti-retour (6) dans l'état d'ouverture et présentant un côté flux entrant et un côté flux sortant de l'agent hydraulique. Afin de concevoir de façon avantageuse une telle presse hydraulique en ce qui concerne la réaction de la soupape de commande, il est prévu selon l'invention que la soupape de commande (7) soit sollicitée lors de l'ouverture du clapet anti-retour (6) par la pression de l'agent hydraulique refluant sur le côté flux entrant et le côté flux sortant, la pression étant plus faible sur le côté flux entrant en raison du rétrécissement.
EP10727433A 2009-07-02 2010-07-01 Dispositif de pressage hydraulique Active EP2448720B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL10727433T PL2448720T3 (pl) 2009-07-02 2010-07-01 Prasa hydrauliczna

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE102009031678 2009-07-02
DE102009026273A DE102009026273A1 (de) 2009-07-02 2009-07-29 Hydraulisches Pressgerät
PCT/EP2010/059356 WO2011000907A1 (fr) 2009-07-02 2010-07-01 Presse hydraulique

Publications (2)

Publication Number Publication Date
EP2448720A1 true EP2448720A1 (fr) 2012-05-09
EP2448720B1 EP2448720B1 (fr) 2013-03-20

Family

ID=43298832

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10727433A Active EP2448720B1 (fr) 2009-07-02 2010-07-01 Dispositif de pressage hydraulique

Country Status (12)

Country Link
US (1) US8844436B2 (fr)
EP (1) EP2448720B1 (fr)
KR (1) KR101821238B1 (fr)
CN (1) CN102481689B (fr)
AU (1) AU2010268021B2 (fr)
BR (1) BRPI1015945A2 (fr)
DE (1) DE102009026273A1 (fr)
ES (1) ES2411881T3 (fr)
MX (1) MX2012000079A (fr)
PL (1) PL2448720T3 (fr)
RU (1) RU2532224C2 (fr)
WO (1) WO2011000907A1 (fr)

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Publication number Priority date Publication date Assignee Title
EP2835540A1 (fr) 2013-08-08 2015-02-11 HAWE Hydraulik SE Entraînement hydraulique

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US20120160065A1 (en) 2012-06-28
KR101821238B1 (ko) 2018-01-23
AU2010268021B2 (en) 2014-07-10
MX2012000079A (es) 2012-02-29
US8844436B2 (en) 2014-09-30
CN102481689B (zh) 2014-12-10
PL2448720T3 (pl) 2013-07-31
RU2532224C2 (ru) 2014-10-27
EP2448720B1 (fr) 2013-03-20
WO2011000907A1 (fr) 2011-01-06
AU2010268021A1 (en) 2012-02-02
ES2411881T3 (es) 2013-07-09
KR20120052957A (ko) 2012-05-24
DE102009026273A1 (de) 2011-01-05
BRPI1015945A2 (pt) 2016-04-19
CN102481689A (zh) 2012-05-30
RU2012103481A (ru) 2013-08-10

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