EP2682610A1 - Système de réglage d'une pompe hydraulique à débit variable - Google Patents

Système de réglage d'une pompe hydraulique à débit variable Download PDF

Info

Publication number
EP2682610A1
EP2682610A1 EP12174666.3A EP12174666A EP2682610A1 EP 2682610 A1 EP2682610 A1 EP 2682610A1 EP 12174666 A EP12174666 A EP 12174666A EP 2682610 A1 EP2682610 A1 EP 2682610A1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
control system
pilot valve
line
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
EP12174666.3A
Other languages
German (de)
English (en)
Other versions
EP2682610B1 (fr
Inventor
Georg Dipl.-Ing. Jemüller
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
Original Assignee
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 EP12174666.3A priority Critical patent/EP2682610B1/fr
Publication of EP2682610A1 publication Critical patent/EP2682610A1/fr
Application granted granted Critical
Publication of EP2682610B1 publication Critical patent/EP2682610B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • 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
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • F15B11/055—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive by adjusting the pump output or bypass
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate

Definitions

  • the invention relates to a control system of a hydraulic variable displacement pump according to the preamble of patent claim 1.
  • the pilot valve assumes a throttling control position, so that pressure fluid is discharged from the signal pressure line in the return line, as well as the pilot valve for pressure control.
  • This means a loss which increases relative to the pump flow, the farther the pump is moved towards the minimum delivery, and may for example be about 2 to 3 l / min, so that then the pump has to work increasingly for loss compensation. This significantly degrades the volumetric efficiency.
  • variable pumps are pressure-controlled via the main stage and the pilot valve, either with adjustable pressure directly to the pump to keep the system pressure constant with varying flow requirements, for example in constant-pressure systems in which different flow rates are required, or as a low-loss pressure limitation of a hydraulic system.
  • the main stage can be operated as a load-sensing controller, for example with integrated pressure limitation of the system pressure, independent of the load pressure, wherein a load pressure signal of at least one consumer supplied by the variable displacement pump is fed into the signal pressure line and to the pilot valve.
  • a torque controller for example, to keep the product of pressure x flow constant, this torque controller is adjustable in a certain percentage of the drive torque of the variable displacement pump.
  • pilot valve a 2/2-way pressure control valve, for example with actuation by a proportional solenoid, it being possible to control the flow rate directly or indirectly proportional to the bias current of the proportional solenoid, that is, the flow rate with increasing Beaufschlagungsstrom for example, to increase linearly or to decrease linearly.
  • a proportional solenoid for example, the flow rate with increasing Beaufschlagungsstrom for example.
  • There may be more than one unilaterally acted actuator cylinder can be provided.
  • differential cylinder with double-sided pressurization, or an eccentric cradle can be used to adjust the pump.
  • the pilot valve allows pressure medium to flow out of the signal pressure line to the return line, which means a relatively increasing loss in the direction of the minimum displacement adjustment pump, which degrades the volumetric efficiency.
  • the invention has for its object to improve a control system of a hydraulic variable displacement pump, which is operated with volume control and / or torque control and a single main stage, in terms of volumetric efficiency.
  • the pressure medium discharged from the signal pressure line during the control does not flow as a loss into the return line but into the already lower pressure range of the actuating cylinder, so that Here, a pressure medium circuit is created, which is largely closed. Since there is a constantly adapting pressure level when the adjusting cylinder is pressurized, the torque and / or quantity control may possibly also be more stable than when the pressure medium is discharged into the substantially uniform, extremely low pressure level of the return line. Since thus drained pressure medium is not lost, despite the small-sized, cost-effective and lightweight Control system of the volumetric efficiency of the variable, for example, then significantly improved when the variable displacement is increasingly adjusted towards minimum funding.
  • the quantity pilot valve is adjustable by a proportional solenoid against spring force either to a passage position (the delivery increases directly proportional to the charge current of the proportional solenoid) or a blocking position (the flow rate per unit time decreases indirectly proportional to the charge current of the proportional solenoid) 2 / 2-way pressure control valve.
  • a proportional solenoid against spring force either to a passage position (the delivery increases directly proportional to the charge current of the proportional solenoid) or a blocking position (the flow rate per unit time decreases indirectly proportional to the charge current of the proportional solenoid) 2 / 2-way pressure control valve.
  • the application current of the proportional solenoid specifies the desired value of the quantity to be regulated. This setpoint specification could alternatively, e.g. on the pilot valve, hydraulically, pneumatically, by spring force, or otherwise done.
  • the torque control and / or the pressure control pilot valve is a pressure-controlled from the signal pressure line forth against spring force toward a passage position 2/2 pressure relief valve.
  • pilot valve types fulfill the control function for the pilot pressure of the main stage under spring force.
  • embodiments of the control system are possible in which e.g. in addition to the pressure regulator pilot valve only the flow control pilot valve or only the torque control pilot valve are provided.
  • the torque control is suitably adjustable by the spring-control pilot valve in the direction of a locking position acting spring force is adjustable.
  • the torque control (or power control) intervenes, for example, only from a selectable pressure level within the usable pressure range and then to the maximum pressure to reduce the flow rate after a predetermined curve.
  • the spring force of the flow control and / or torque control pilot valve is generated by a spring and by a position feedback feedback, preferably the actuating cylinder, changeable.
  • a position feedback feedback preferably the actuating cylinder, changeable.
  • the spring force can be changed with increasing adjustment of the pump in the direction of minimum delivery, for example, increased.
  • the return takes place by tapping off the position of the first actuating cylinder via a cam surface and a button that changes the set spring preload or spring force.
  • the feedback can also be done by using a displacement transducer, a pressure sensor, an angle sensor of the swash plate, etc. In this way, the control loop is simply closed via the pilot valve.
  • the pressure in the signal pressure line can be generated by means of an inlet nozzle from the pressure line leading to the main stage in the control system itself and modified if necessary.
  • the signal pressure line may be connected to a load pressure signal circuit of at least one consumer powered by the pump and separated from the pressure line.
  • a control line is connected to the actuating cylinder between the main stage and the actuating cylinder via a nozzle to the return line.
  • the consequent loss of pressure medium is negligible.
  • the 3/2-way pressure control valve of the main stage in the direction of adjustment for connecting the pressure line and the first actuating cylinder from the pressure line ssenvorteil, that is from the delivery pressure of the variable itself, and pressure controlled in the direction of the connection of the first actuating cylinder with the return line from the signal pressure line and spring loaded.
  • This spring load is conveniently adjustable, z. B. to produce a constant pressure level below the set by the system pressure relief valve pressure levels in variations of the flow rate.
  • At least one second actuating cylinder may be loaded from the pressure line and spring-biased, e.g. in such a way that the variable-speed pump starts up with maximum delivery during commissioning, for example before the control system intervenes.
  • variable displacement pump equipped with the control system is a swashplate type axial piston pump, for example with a nominal pressure of up to about 350 bar, a maximum pressure of about 400 bar, and type-dependent with a displacement volume of 60, 90 or 110 cm 3 / rev.
  • This design is robust and reliable and designed for flanging on power take-offs of commercial vehicle transmissions or for a standard connection with an SAE flange, and is universally suitable for other applications.
  • the design has a high Denansaugnaviere and a low sound pressure level.
  • the volume flow is proportional to the speed and the current displacement volume and can be infinitely adjusted.
  • Such variable displacement pumps are particularly suitable for use with proportional directional slides and can be operated with alternating direction of rotation.
  • the actuating cylinders engage e.g. together on a swash plate adjusting.
  • the actuating cylinders are arranged in pairs and connected in parallel.
  • this actuating cylinder has a larger pressurization surface than every second actuating cylinder.
  • the area ratio may be between about 2: 1 to 5: 1, or even greater, controlling the pressure fluid discharged to the actuator cylinder very precisely.
  • the pilot valves for pressure and / or torque control may e.g. Be slide valves.
  • a control system S of a hydraulic variable-displacement pump V is arranged, for example, with a control system housing 9 on or in a variable-displacement pump housing 1.
  • the variable displacement pump V is, for example, a swashplate axial piston pump 2, whose volumetric flow is steplessly adjustable in the direction of a double arrow between maximum delivery and minimum delivery by means of a swash plate adjusting element 3.
  • At least one actuating cylinder Z1 (and optionally a second actuating cylinder Z2) engages on the adjusting element 3.
  • FIG Fig. 1 is a parallel-connected pair of first actuating cylinder Z1, Z1 'and a parallel pair of second actuating cylinder Z2, Z2' provided.
  • sensors 35 transducers, angle sensors, pressure sensors, or the like
  • sensors 35 could be used for reporting, e.g.
  • at least one double-acting differential adjusting cylinder could be used to adjust the pump, or an eccentric cradle (not shown).
  • Each actuating cylinder Z1, Z1 ' is connected at its pressurization side to a control line 7.
  • the second actuating cylinders Z2, Z2 'further comprise springs 34, that is, are spring-biased to the variable displacement pump V as by the pressurization from the pressure line 8, for. in the direction of maximum promotion.
  • a pressurization of the actuating cylinder Z1, Z1 'then takes an adjustment in the direction of minimum funding.
  • a pressure port 10 is indicated (X, LS) on which a signal pressure in a signal pressure line 21 can either be measured or fed, for example, from a load pressure signal circuit LS of the consumer M, comes ( Fig. 2 ).
  • a signal pressure in a signal pressure line 21 can either be measured or fed, for example, from a load pressure signal circuit LS of the consumer M, comes ( Fig. 2 ).
  • the pressure in the signal pressure line 21 from the control system S itself adjustable.
  • the control system S includes a single main stage 11, which is designed as a 3/2-way control valve and connected to the pressure line 8 and a return line 19 on the one hand and to the control line 7 on the other.
  • the 3/2-way pressure control valve 12 is pressure-controlled from the pressure line 8 via a pilot line 16 and from the signal pressure line 21 via a pilot line 13, wherein on the side of the pilot line 13, a spring force 15 is effective, which is, suitably, adjustable ,
  • the 3/2-way pressure control valve 12 is switched after startup of the variable V in the setting for maximum promotion from the switching position shown in another switching position in which the pressure line 8 is connected to the control line 7 and the return line 19 is shut off , so that the adjusting cylinders Z1, Z1 'are pressurized and adjust the variable displacement pump V in the direction of minimum promotion, against the force of the pressurization of the second actuating cylinder Z2, Z2 'from the pressure line 8 and the biasing springs 34.
  • the pressurization surface of each first actuating cylinder Z1, Z1' is expediently larger than the pressurization surface of the second actuating cylinder Z2, Z2 '(area ratio eg between 2: 1 to 5: 1 or greater).
  • the line 22 leads to a pressure control pilot valve 34 (with suitably adjustable spring force), from the drain side, a line 31 via a node 32 to a node 33 of the control line 7 leads.
  • a line 23 branching off from the line 22 leads to an inlet side of a quantity control pilot valve 24.
  • the line 22 ' leads to the inlet side of a torque control pilot valve 25, which is pressure-controlled from the line 22' against a spring force 22 and 2/2 Way drain valve may be formed.
  • the flow control pilot valve 24 is a 2/2-way pressure control valve, which is actuated by a proportional solenoid 26 against spring force 28, and, preferably, even a proportional pressure pilot 27 may have.
  • the proportional solenoid 26 actuates the valve 24 in the direction of a passage position against the spring force 28 which adjusts a shut-off position.
  • the energization of the proportional magnet 26 is a desired value specification for the quantity control. This set point specification could also be made hydraulically, mechanically, pneumatically or otherwise (not shown).
  • the pilot valves 25, 24, 34 are each connected at the outlet side to the node 32 and thus via the line 31 to the node 33 in the control line 7 and the respective actuating cylinder Z1, Z1 'connected to feed according to the invention pressure medium there, so that this pressure medium from the signal pressure line 21 is not lost.
  • the pilot valves 24, 25, 34 (or only 24 or 25 and 34) are associated with the main stage 11 and in the embodiment shown in FIG Fig. 1 the pressure difference generated by the inlet nozzle 14 for the main stage 11th
  • the pilot valve 24 is, as long as the proportional solenoid 26 is not energized, in the shut-off position, and has no influence on the pressure in the signal pressure line 21. If the proportional solenoid 26 is energized, then the pilot valve 24 reduces the pressure in the signal pressure line 21, with increasing Adjustment of the actuating cylinder Z1, Z1 'eg in the direction of the minimum promotion of the variable V increases the spring force 28 and thus the pressure in the signal pressure line 21 is increased again with constant energization of the proportional magnet 26.
  • FIG. 2 shown detail variant ends the pressure line 8 to the main stage 11 and the pressure in the signal pressure line 21, for example, from the load pressure signal circuit LS used to adjust the main stage 11 against the pressure in the pilot line 16 from the pressure line 8.
  • Fig. 3 In the detail variant in Fig. 3 is the pilot valve 24 'connected inversely to flow control as in Fig. 1 that is, the spring force 28 holds the control valve 24 'in the passage position shown, while the proportional solenoid 26 causes an adjustment in the direction or to the shut-off when energized against the spring force 28.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
EP12174666.3A 2012-07-02 2012-07-02 Système de réglage d'une pompe hydraulique à débit variable Active EP2682610B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP12174666.3A EP2682610B1 (fr) 2012-07-02 2012-07-02 Système de réglage d'une pompe hydraulique à débit variable

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP12174666.3A EP2682610B1 (fr) 2012-07-02 2012-07-02 Système de réglage d'une pompe hydraulique à débit variable

Publications (2)

Publication Number Publication Date
EP2682610A1 true EP2682610A1 (fr) 2014-01-08
EP2682610B1 EP2682610B1 (fr) 2015-12-09

Family

ID=46507877

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12174666.3A Active EP2682610B1 (fr) 2012-07-02 2012-07-02 Système de réglage d'une pompe hydraulique à débit variable

Country Status (1)

Country Link
EP (1) EP2682610B1 (fr)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104179734A (zh) * 2014-08-27 2014-12-03 浙江德泰机电工程有限公司 一种用于液压泵的恒压控制装置及控制方法
DE102017202899B4 (de) 2017-02-22 2022-01-05 Hawe Hydraulik Se Regelsystem für eine Hydraulik-Verstellpumpe, Pumpenaggregat und Hydrauliksystem mit einem Pumpenaggregat
DE102022202279A1 (de) 2022-03-07 2023-09-07 Hawe Hydraulik Se Elektrohydraulische Regelungsvorrichtung und verstellbares hydraulisches Pumpensystem

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018200825B3 (de) 2018-01-18 2019-01-24 Hawe Hydraulik Se Regelsystem für eine Hydraulik-Verstellpumpe, Pumpenaggregat und Fahrzeug mit einem Pumpenaggregat

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH431221A (de) * 1964-10-02 1967-02-28 Buehler Ag Geb Hydrostatischer Antrieb

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH431221A (de) * 1964-10-02 1967-02-28 Buehler Ag Geb Hydrostatischer Antrieb

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
HAWE HYDRAULIK SE, MÜNCHEN: "Axialkolben-Verstellpumpe Typ V60N, Serie 03", 31 July 2011 (2011-07-31), XP055045755, Retrieved from the Internet <URL:http://www.hawe.de/fileadmin/content/typeman/catalog/Pdf/7/9/D7960N-de.pdf> [retrieved on 20121127] *

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104179734A (zh) * 2014-08-27 2014-12-03 浙江德泰机电工程有限公司 一种用于液压泵的恒压控制装置及控制方法
DE102017202899B4 (de) 2017-02-22 2022-01-05 Hawe Hydraulik Se Regelsystem für eine Hydraulik-Verstellpumpe, Pumpenaggregat und Hydrauliksystem mit einem Pumpenaggregat
DE102022202279A1 (de) 2022-03-07 2023-09-07 Hawe Hydraulik Se Elektrohydraulische Regelungsvorrichtung und verstellbares hydraulisches Pumpensystem

Also Published As

Publication number Publication date
EP2682610B1 (fr) 2015-12-09

Similar Documents

Publication Publication Date Title
EP3567167B1 (fr) Dispositif de commande hydraulique pour un ensemble de machines de travail mobiles et ensemble de machines de travail mobiles
EP1644643B1 (fr) Dispositif et procede de commande d&#39;au moins deux recepteurs hydrauliques
EP0584078B1 (fr) Dispositif de protection contre les surcharges pour un moteur d&#39;entrainement d&#39;une pompe principale d&#39;une unite hydraulique d&#39;alimentation en pression
EP1701042B1 (fr) Commande hydraulique
DE3535771C2 (fr)
EP2307726B1 (fr) Pompe à cylindrée variable
DE102010020004A1 (de) Regelungsvorrichtung und Verfahren zur Regelung eines Drehmoments einer Triebwelle einer hydrostatischen Maschine
DE102013214807A1 (de) Hydrostatischer Antrieb, insbesondere hydrostatischer Lüfterantrieb
EP2682610B1 (fr) Système de réglage d&#39;une pompe hydraulique à débit variable
DE102019208086A1 (de) Hydraulisches Antriebssystem mit zwei Pumpen und Energierückgewinnung
EP1989450A1 (fr) Dispositif de commande hydraulique
DE102013214861A1 (de) Verstellvorrichtung für eine hydrostatische Pumpe und hydrostatische Pumpe
DE3443354A1 (de) Hydraulikanlage
EP0471166B1 (fr) Dispositif de contrôle pour le réglage de l&#39;ajustement du débit de plusieurs pompes hydrostatiques réglables
EP0561153B1 (fr) Dispositif de réglage de puissance pour au moins deux pompes hydrostatiques à débit variable
EP1170510B1 (fr) Agencement de contrôle hydraulique pour alimenter en fluide sous pression de préférence plusieurs utilisateurs hydrauliques
DE102010020528B4 (de) Hydrostatischer Antrieb
DE3844399C2 (de) Steueranordnung für mehrere unabhängig voneinander betätigbare hydraulische Verbraucher und deren Verwendung
EP2337949A2 (fr) Agencement de positionnement hydraulique d&#39;un excentrique pour le réglage d&#39;une cylindrée prédéterminée sur un moteur hydrostatique
DE10138519A1 (de) Hydromotor mit Bremseinrichtung
DE19735110B4 (de) Regelvorrichtung mit Druckmittler
WO2011060929A1 (fr) Agencement hydraulique comprenant une pompe à cylindrée variable et une soupape de décharge
DE10035631C2 (de) Nullastschaltung
DE10035575A1 (de) Hydraulische Steueranordnung zur Druckmittelversorgung von vorzugsweise mehreren hydraulischen Verbrauchern
DE2121267A1 (de) Verstellpumpe mit Verstellvorrichtung

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: 20130114

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20150810

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

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: AT

Ref legal event code: REF

Ref document number: 764711

Country of ref document: AT

Kind code of ref document: T

Effective date: 20151215

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502012005399

Country of ref document: DE

REG Reference to a national code

Ref country code: SE

Ref legal event code: TRGR

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20151209

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

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

Ref country code: NO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160309

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

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160310

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

Ref country code: RS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

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

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 5

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

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

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

Ref country code: SM

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160409

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20160411

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502012005399

Country of ref document: DE

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 502012005399

Country of ref document: DE

Representative=s name: GROSSE, SCHUMACHER, KNAUER, VON HIRSCHHAUSEN, DE

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

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

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

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

Ref country code: IT

Payment date: 20160729

Year of fee payment: 5

26N No opposition filed

Effective date: 20160912

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

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

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

Ref country code: FR

Payment date: 20160725

Year of fee payment: 5

Ref country code: SE

Payment date: 20160725

Year of fee payment: 5

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

Ref country code: BE

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

Effective date: 20160731

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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

Effective date: 20160702

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

Ref country code: MC

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

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

Ref country code: LI

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

Effective date: 20160731

Ref country code: CH

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

Effective date: 20160731

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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: 20160702

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

Ref country code: IE

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

Effective date: 20160702

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

Ref country code: LU

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

Effective date: 20160702

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20180330

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: 20170703

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 502012005399

Country of ref document: DE

Representative=s name: GROSSE, SCHUMACHER, KNAUER, VON HIRSCHHAUSEN, DE

Ref country code: DE

Ref legal event code: R081

Ref document number: 502012005399

Country of ref document: DE

Owner name: HAWE HYDRAULIK SE, DE

Free format text: FORMER OWNER: HAWE HYDRAULIK SE, 81673 MUENCHEN, DE

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: 20170731

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO

Effective date: 20120702

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

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

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

Ref country code: HR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

Ref country code: MT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

Ref country code: MK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

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

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

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: 20170702

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 764711

Country of ref document: AT

Kind code of ref document: T

Effective date: 20170702

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

Ref country code: AL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20151209

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

Ref country code: AT

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

Effective date: 20170702

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230523

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

Ref country code: DE

Payment date: 20230720

Year of fee payment: 12