EP2553231B1 - Entraînement hydraulique de ventilateur - Google Patents

Entraînement hydraulique de ventilateur Download PDF

Info

Publication number
EP2553231B1
EP2553231B1 EP11718903.5A EP11718903A EP2553231B1 EP 2553231 B1 EP2553231 B1 EP 2553231B1 EP 11718903 A EP11718903 A EP 11718903A EP 2553231 B1 EP2553231 B1 EP 2553231B1
Authority
EP
European Patent Office
Prior art keywords
pressure
hydraulic
hydraulic motor
control
fan drive
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.)
Not-in-force
Application number
EP11718903.5A
Other languages
German (de)
English (en)
Other versions
EP2553231A2 (fr
Inventor
Michael Schuette
Tobias Pfruender
Martin Fassbender
Egon Rill
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2553231A2 publication Critical patent/EP2553231A2/fr
Application granted granted Critical
Publication of EP2553231B1 publication Critical patent/EP2553231B1/fr
Not-in-force 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
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/02—Units comprising pumps and their driving means
    • F04D13/04—Units comprising pumps and their driving means the pump being fluid driven
    • F04D13/046—Units comprising pumps and their driving means the pump being fluid driven the fluid driving means being a hydraulic motor of the positive displacement type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/02—Controlling of coolant flow the coolant being cooling-air
    • F01P7/04—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio
    • F01P7/044—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio using hydraulic drives

Definitions

  • the invention is based on a hydraulic fan drive, which has a variable in its stroke hydraulic pump, which is associated with a pressure control valve arrangement for adjusting a pump pressure by adjusting the stroke volume, a hydraulic motor for driving a fan and a pressure line which is connected to a pressure input of the hydraulic motor and in which by the hydraulic pump pressure medium is conveyed.
  • Such fan drives are mainly used in construction machinery, agricultural and forestry machinery, in conveyor technology, in trucks and buses and in rail vehicles.
  • Such a fan drive is for example from the DE 43 21 637 A1 known.
  • the pressure-controlled hydraulic pump is operated with a hydraulic motor of constant displacement in an open hydraulic circuit.
  • the pressure regulating valve assembly consists essentially of a control valve with a connected to the pressure output of the hydraulic pump pressure port to which the pump pressure is present, a tank connected to a tank port and connected to the control chamber on a control piston control connection, an electroproportional adjustable, directly controlled pressure relief valve and a nozzle disposed between the pressure outlet of the hydraulic pump and the inlet of the pressure relief valve.
  • the control piston of the control valve is in the sense of a fluidic connection of the pressure output of the hydraulic pump and in the sense of reducing the stroke volume (flow rate per revolution) of the hydraulic pump with the control connection from the pump pressure and in the sense of a fluidic connection of the control connection to the tank connection and in the sense of increasing the Hubvolumens acted upon by a spring and the pressure applied to the inlet of the pressure relief valve.
  • the invention has for its object to further develop a hydraulic fan drive with the features of the preamble of claim 1 so that it can be used for the recuperation of energy.
  • a hydraulic accumulator is connected and the hydraulic motor is adjustable in its displacement.
  • a hydraulic fan drive according to the invention can be cached due to the hydraulic accumulator connected to the pressure line by feeding pressure medium beyond the amount that is swallowed by the hydraulic motor, the energy in other operations on the machine, for example during a braking operation or when lowering a Load, free.
  • the pressure changes in the pressure line associated with the intermediate storage and the release of energy can be compensated by changing the absorption volume of the hydraulic motor so that the torque delivered by the hydraulic motor corresponds to the desired fan speed.
  • the hydraulic accumulator is preferably connected directly to the pressure line without actuated valves.
  • Additional energy can for example be fed directly through the hydraulic pump, if according to claim 2, the setting of the pressure control valve assembly is remotely modifiable.
  • the pressure regulating valve assembly is advantageously set at a pressure midway between the maximum and minimum accumulator operating pressures. Now, if the pressure control valve assembly is set to a higher pressure, so can Example in a braking operation or a sudden relief of the hydraulic pump driving diesel engine to the speed protection additional pressure medium are fed into the hydraulic accumulator. The increased pressure level is compensated by a reduction in the displacement of the hydraulic motor, so that the fan speed does not change.
  • a check valve is arranged, which closes to the hydraulic pump out, so regardless of the hydraulic pump and regardless of their pressure setting at a higher pressure level Pressure medium to be fed into the pressure line.
  • a branch line which opens into the pressure line.
  • a check valve which opens to the portion of the pressure line.
  • the pressure in the branch line upstream of the check valve may also be smaller than the pressure in the pressure line or even tank pressure.
  • the cached energy can be used to drive the hydraulic motor, wherein in the presence of a check valve at the pump outlet, an adjustable pressure control valve assembly after the injection of additional pressure medium quantity can be reset to the original value.
  • a check valve at the pump outlet
  • an adjustable pressure control valve assembly after the injection of additional pressure medium quantity can be reset to the original value.
  • the pressure regulating valve arrangement is set slightly higher than the current storage pressure. This can also be achieved by a slow time-dependent withdrawal of the control signal for the pressure regulating valve arrangement.
  • the hydraulic pump is an adjustable over zero hydraulic pump, so that it is operable as a hydraulic motor with the same pressure connection and the same direction of rotation.
  • the power output can be smoothed or kept constant by the diesel engine.
  • the pressure regulating valve arrangement can also be set to values below the normal pressure level, so that in order to support the diesel engine or in general an internal combustion engine or even an electric motor (primary unit) is particularly high energy available.
  • the hydraulic motor can even be set to zero displacement, so that although the fan is not driven for a short time, but the entire stored energy is available for the support of the primary unit.
  • the primary unit is spared due to a more uniform load and thus has a more favorable consumption of primary energy.
  • the hydraulic motor is assigned a torque control valve arrangement for regulating an engine torque by adjusting the intake volume.
  • the hydraulic motor then adjusts itself to the displacement volume at a given control signal, which results in the torque which corresponds to the desired speed of the fan wheel in the pressure prevailing in the pressure line and in the hydraulic accumulator. This is automatically compensated for pressure fluctuations.
  • the torque characteristic can be shifted in parallel. It is also a particularly simple parallel arrangement of multiple torque-controlled fan motors for driving multiple fan wheels possible.
  • the torque control valve arrangement is preferably designed according to claim 9.
  • the hydraulic motor may also be associated with a control valve arrangement with which the displacement of the hydraulic motor is variable in proportion to a control signal, wherein the control signal on the one hand by a speed setpoint of the hydraulic motor and on the other hand by a detected speed of the hydraulic motor or the detected pressure in the Pressure line is dependent. From the detected speed can be seen directly by comparison with the target speed, whether the displacement must be increased or decreased. From the detected pressure and the target speed, the target intake volume can be calculated and specified.
  • FIG. 1 belongs to the hydraulic fan drive a first hydraulic machine 10, which is so called because it is operable both as a hydraulic pump and as a hydraulic motor.
  • the hydraulic machine 10 is mechanically connected to a diesel engine 11. It has a high-pressure connection (pressure connection) 12 and a low-pressure connection (tank connection) 13, which is permanently connected to a tank 9. From the pressure port 12, a pressure line 14 leads to a hydraulic motor 15, from which a fan 16 is driven. To the pressure line directly a hydraulic accumulator 17 is connected, which can be operated for example in a pressure range between 100 bar and 300 bar and is charged in normal operation to 200 bar.
  • the hydromachine is, for example, an axial piston machine of swashplate type and adjustable with its displacement between a maximum positive value and a maximum negative value above zero.
  • the hydraulic machine promotes 10 as a hydraulic pump pressure medium in the pressure line 14.
  • negative displacement the hydraulic machine operates at the same Direction of rotation as a hydraulic motor and is supplied from the pressure line 14 with pressure medium.
  • actuating pistons and a spring are provided, of which a relative to the other actuating piston has a larger effective surface exhibiting actuating piston 18 a control chamber 19, the pressure medium can be supplied and discharged from the pressure medium.
  • This supply and removal of pressure medium is controlled by a built-up on the hydraulic machine 10 pressure control valve assembly 20.
  • This includes a continuously adjustable control valve 21 with a zero coverage or small positive overlap between the control edges and with a pressure port 22, the fluidic with the pressure port 12 of the hydraulic machine 10 is connected to a tank connection 23 which is connected via the interior of the housing of the hydraulic machine 10 with a leak oil connection 30, and with a control connection 24 which is connected via a damping nozzle 25 with the adjusting chamber 19.
  • the valve piston of the control valve is in the sense of a connection of the control port 24 to the pressure port 22 and in the sense of reducing the stroke volume of the hydraulic machine 12 to negative values of the pump pressure and in the sense of connecting the control port 24 to the tank port 23 and in the sense of an increase of the stroke volume acted upon by a spring 26 and by a variable control pressure, which is tapped between a control oil 27 and a pressure-limiting valve 28 proportionally adjustable by an electromagnet 29, that is corresponds to the set value of the pressure relief valve.
  • control valve If the control valve is in the control position, in which the valve piston makes at most small movements about a middle position, then the control oil flow is always the same regardless of the pressure level, since then the pressure in the pressure connection of the hydraulic machine is always higher than the pressure equivalent of the spring 26 Control pressure and thus the pressure difference across the nozzle 27 is always the same.
  • the pressure relief valve 28 has a falling characteristic, the pressure at its input is therefore the lower, the stronger the Electromagnet 29 is energized. This has the consequence that in case of failure of the electrical system, the pressure relief valve has its maximum setting and according to the pressure at the pressure port of the hydraulic machine 12 is maximum.
  • the hydraulic motor 15 is preferably of axial piston design, in particular of a bent-axis design, and is adjustable between a displacement of zero and a maximum displacement. It is connected to the pressure line 14 with a pressure connection 35 and connected to the tank 9 via a tank connection 36. To change the absorption volume, the hydraulic motor 15 has an actuating piston 37, which is provided on one side with a piston rod 38 and thus a piston rod-side annular space 39 and a piston rod-side actuating chamber 40 from each other.
  • the inflow and outflow of pressure medium from the control chamber 40 is controlled by a solenoid 41 proportionally acted upon control valve 42, which is constructed on the hydraulic motor 15 and a pressure port 43 which is connected to the pressure port 35, a tank port 44, via the Inside the housing of the hydraulic motor and a unspecified leakage connection with tank 9 is connected, and a control port 45 which is connected to the adjusting chamber 40.
  • the annular space 39 is connected via the unspecified housing of the control valve 42 permanently fluidly connected to the pressure port 35.
  • the electromagnet 41 acts on a control piston of the control valve 42 in the sense of a connection of the control connection 45 with the pressure connection 43 and in the sense of reducing the absorption volume of the hydraulic motor 15.
  • the control piston In the sense of connecting the control connection to the tank connection 44, the control piston is actuated by a first spring 46, which is supported fixed to the housing and by the beginning of the rule is adjustable, and acted upon by a second spring 47 which is disposed between the control piston and the piston rod 38, so the adjusting piston 37.
  • This structure causes the position of the actuating piston and thus the displacement of the hydraulic motor 15 directly from the force of the electromagnet 41, that depends on the amount of current flowing through the coil of the electromagnet current.
  • the actuating piston In a regulated state, on the one hand, the actuating piston must be at rest and, on the other hand, an equilibrium of forces prevails at the control piston of the control valve, which is located in its control position independently of the position of the actuating piston.
  • the sum of the forces exerted by the two springs 46 and 47 must therefore be equal to the force of the electromagnet 41.
  • the force of the spring 46 is always the same in the control position of the control piston. So depending on the magnetic force, the force of the spring 47 must be different. This different force of the spring 47 results from the different depending on the magnetic force positions of the actuating piston 37. This type of adjustment is also known as electro-proportional adjustment.
  • the speed of the hydraulic motor 15 and thus that of the fan 16 is detected by a speed sensor 50, which outputs a corresponding signal to an electrical control unit 51. This is also fed to a speed setpoint, which is determined from the temperature of a medium to be cooled.
  • the control unit 51 now controls the electromagnet 41 in such a way that the desired rotational speed is achieved on the basis of the self-adjusting absorption volume.
  • a pressure sensor 52 may also be provided with which the pressure in the pressure line 14 is detected. With a fan, there is a fixed relationship between the drive torque and the speed. The pressure can thus be used to calculate the displacement required to apply the drive torque required to reach or maintain the desired speed and to control the solenoid accordingly.
  • the hydraulic machine 10 operates as a hydraulic pump and is set, for example, to a pressure value of 150 bar. This pressure prevails the pressure line 14 and the hydraulic accumulator 17. The displacement of the hydraulic motor 15 is now adjusted so that at the pressure of 150 bar, the necessary for driving the fan at the desired speed drive torque is obtained. If the electrical system fails, the hydraulic machine is set to maximum pressure and the hydraulic motor to maximum displacement, so that sufficient cooling of the medium to be cooled is ensured in each case.
  • the setting of the pressure value on the hydraulic machine 10 and thus the state of charge of the hydraulic accumulator 17 can be changed in order, for example, to be able to operate the hydraulic motor 15 predominantly with a large displacement or to smooth out the power to be delivered by the diesel engine 11. If the diesel engine is just under-demanded, the pressure level can be increased for a short time, for a short time it can be lowered. By increasing the pressure level, the diesel engine can be protected from overspeeding.
  • the braking energy can be used by the hydraulic machine 10 is driven as a hydraulic pump by the vehicle itself. It can be set to a maximum pressure, so that the hydraulic machine 10 goes to maximum swing angle and the braking effect of the maximum displacement and the instantaneous pressure in the hydraulic accumulator results.
  • a pressure which is lower than the pressure in the hydraulic accumulator is set by appropriate energization of the electromagnet 29, so that the hydraulic machine pivots above zero to the maximum negative displacement volume and supports the diesel engine as working as a hydraulic motor until the accumulator pressure has dropped to the pressure set on the hydraulic machine 10.
  • Previously stored in the hydraulic accumulator braking energy can therefore be used to boost the diesel engine. Likewise, however, their use for supplying the hydraulic motor 15 and thus for driving the fan is possible.
  • the pressure set on the hydraulic machine should then be lowered so slowly, taking into account the quantity of pressure medium swallowed by the hydraulic motor 15, that the set pressure is not lower than the accumulator pressure.
  • the hydraulic pump 60 which is mechanically connected via a coupling with a primary unit 61 and can be driven by this.
  • Engine operation is not provided for the engine 60 here.
  • the hydraulic pump has a pressure port 62 and a suction port 63 which is permanently connected to a tank 9.
  • a pressure line 14 leads to a hydraulic motor 65, from which a fan 16 is driven.
  • a hydraulic accumulator 17 is connected, which can be operated for example in a pressure range between 100 bar and 300 bar.
  • a check valve 66 which blocks the hydraulic pump 60 out.
  • the hydraulic pump 60 is, for example, a swash plate type axial piston pump.
  • the pressure medium can be supplied and discharged from the pressure medium.
  • a hydraulic control valve assembly 70 constructed on the hydraulic pump 60.
  • a hydraulic control valve assembly 70 constructed on the hydraulic pump 60.
  • a continuously variable control valve 71 with a zero overlap or small positive overlap between the control edges and with a pressure port 72, fluidly connected to the pressure port 62 of the hydraulic pump 60 is connected to a tank port 73, which is connected via the interior of the housing of the hydraulic pump 60 with a drain port 67, and with a control port 74 which is connected to the actuating chamber 19.
  • the valve piston of the control valve is in the sense of a connection of the control connection 74 with the pressure port 62 and in the sense of reducing the stroke volume of the hydraulic pump 60 from the pump pressure and in the sense of connecting the control port 74 to the tank port 73 and in terms of increasing the stroke volume of only one Spring 75 acted upon.
  • a pressure is established at the pressure connection 62 of the hydraulic pump 60, which corresponds to the pressure equivalent of the spring 75, for example a pressure of 100 bar.
  • a remote adjustment of this pressure is - unlike in the embodiment according to FIG. 1 - not provided.
  • the setting of the spring 75 can be changed.
  • the hydraulic motor 65 is preferably of an axial piston design, in particular in a bent-axis design, and as the hydraulic motor 15 of the embodiment according to FIG. 1 adjustable between a zero swallowing volume and a maximum swallowing volume. It is connected to the pressure line 14 with a pressure connection 76 and connected to the tank 9 via a tank connection 77. To change the absorption volume, the hydraulic motor 15 has an actuating piston 78, which is provided on one side with a piston rod 79 and thus a piston rod-side annular space 80 and a piston rod-side actuating chamber 81 from each other.
  • the inflow to and the outflow of pressure medium from the control chamber 81 is controlled by a torque control valve assembly 69 having a control valve 82 which is constructed on the hydraulic motor 65 and a pressure port 83 which is connected to the pressure port 76, a tank port 84, via the Inside the housing of the hydraulic motor and a unspecified leakage connection with tank 9 is connected, and a control connection 85 which is connected to the actuating chamber 81.
  • the annulus 80 is permanently fluidly connected to the pressure port 76.
  • a control piston 82 of the control valve 82 is in the sense of a connection of the control connection 85 to the tank port 84 and in the sense of increasing the absorption volume of the hydraulic motor 65 by a spring 86 which is supported fixed to the housing, and acted upon via a control line 87 by a variable control pressure over the
  • a remotely controlled variable force can be exerted on the control piston.
  • the control pressure is maximum when the electrical system fails.
  • a connection of the control connection to the pressure port 83 of the control piston is acted upon by a force which depends on the position of the actuating piston 78 and thus the displacement of the hydraulic motor 65 and the pressure in the pressure line 14.
  • control racks are initially supported in a control position always the same distance from a housing-fixed axis of rotation of a lever 88 on this lever 88 from.
  • the lever 88 is acted upon by a rod 89 which is movably inserted into the adjusting piston 78 and at which the pressure prevails, which prevails in the pressure line 14.
  • the torque generated by the rod 89 on the lever 88 thus forms the product of the pressure applied to the hydraulic motor 65 and the displacement of the hydraulic motor and thus the output torque of the hydraulic motor.
  • An opposite torque on the lever 88 generates the sum of the forces exerted by the spring 86 and the control pressure on the control piston of the control valve 82.
  • the sum of the torques acting on the lever 88 must be zero. If, for example, the pressure in the pressure line 14 increases, the torque exerted on the lever 88 via the rod 89 becomes greater than the torque exerted via the control piston.
  • the lever is rotated and displaced the control piston, so that the control port 85 is connected to the pressure port 83 of the control valve 82.
  • the actuating chamber 81 flows to pressure medium and the actuating piston migrates towards reduction of the swallow volume. With the actuating piston, the rod 89 moves along the lever 88, so that the lever arm for the pressure force acting on the rod is smaller, until an equilibrium between the torques again exists.
  • the control pressure in the control line 87 does not change, the torque exerted by the hydraulic motor 65 does not change when the pressure level in the pressure line 14 changes. Conversely, by changing the control pressure, the torque and thus the fan speed can be changed.
  • the hydraulic accumulator 17 makes it possible for the amount fed in to be greater than the quantity currently swallowed by the hydraulic motor 65, without the excess amount being hosed off via a pressure-limiting valve.
  • a further, for example, electroproportionally adjustable hydraulic pump 90 is present, which can be coupled via a coupling 91 to the drive train of the vehicle.
  • the clutch is closed and the hydraulic pump 90 is driven by the vehicle and conveys pressure medium into the pressure line 14 via a check valve 92 closing towards it.
  • the advantage here is that it can always be fed in regardless of how high the pressure in the fan circuit is.
  • the feed is shown in the lowering of a load, which is indicated here by a hydraulic cylinder 95.
  • a flow control valve 96 is provided with a proportionally adjustable metering orifice (not shown in detail) and a pressure compensator arranged serially thereto.
  • a branch line 94 between the flow control valve and the pressure line 14 there is a non-return valve for blocking the flow control valve 97.
  • a 2/2 way valve 98 is connected, with which a flow to the tank can be opened.
  • Displaced from the hydraulic cylinder pressure medium can be fed at the desired lowering rate in the pressure line 14 when the load pressure to the pressure drop across the orifice of the flow control valve 96 is higher than the pressure in the pressure line 14 and the hydraulic accumulator 17. It may be that this The beginning of a lowering is given, but not in the further course, since the pressure in the hydraulic accumulator 17 increases. Then the valve 98 must be opened. Whether it is still possible to feed in can be determined with the aid of pressure sensors which record the load pressure and the accumulator pressure. It is also possible to monitor the position of the pressure compensator. When the pressure compensator is fully open, feed-in is no longer possible.
  • the additional amount of pressure medium fed in With regard to the additional amount of pressure medium fed in, one can distinguish two cases. If the quantity of pressure medium fed in is smaller than the consumption by the hydraulic motor 65, the remaining quantity is conveyed by the hydraulic pump 60 and the pressure level in the system remains at the level set at the hydraulic pump 60. Also in this case, an energy saving is achieved because the hydraulic pump 60 pivots to a smaller displacement.
  • the pressure in the fan circuit rises above the level set at the hydraulic pump 60.
  • the hydraulic pump is regulated back to zero stroke by pressure cutoff.
  • the pressure level can now assume a much higher value, for example, 300 bar, until it by a to the pressure line 14th connected pressure relief valve 99 is limited. If nothing is more or only fed less than the hydraulic motor 65 consumed, so first takes over the hydraulic accumulator 17, the full or partial supply of the fan circuit until at a pressure level of 100 bar, the hydraulic pump 60 swings out again.
  • an electronic control of the output torque of the hydraulic motor 65 conceivable, wherein the accumulator pressure detected by a sensor and the displacement is adjusted according to the required torque.
  • FIG. 3 are a hydraulic pump according to the embodiment according to FIG. 1 and a hydraulic motor according to the embodiment according to FIG. 2 combined together.
  • the hydraulic machine 10 is mechanically connected to a diesel engine 11. It has a high-pressure connection (pressure connection) 12 and a low-pressure connection (tank connection) 13, which is permanently connected to a tank 9.
  • a pressure line 14 leads to a hydraulic motor 65, from which a fan 16 is driven.
  • a hydraulic accumulator 17 is connected, which can be operated for example in a pressure range between 100 bar and 300 bar and is charged in normal operation to 200 bar.
  • a pressure limiting valve 99 is connected to the pressure line 14.
  • the hydraulic machine 10 is, for example, an axial piston machine of swash plate type and adjustable with its displacement between a maximum positive value and a maximum negative value above zero. With a positive displacement, the hydraulic machine promotes 10 as a hydraulic pump pressure medium in the pressure line 14. With negative displacement, the hydraulic machine operates at the same direction as a hydraulic motor and is supplied from the pressure line 14 with pressure medium.
  • actuating pistons and a spring are provided, of which a relative to the other actuating piston has a larger effective surface exhibiting actuating piston 18 a control chamber 19, the pressure medium can be supplied and discharged from the pressure medium.
  • This supply and removal of pressure medium is controlled by a built-up on the hydraulic machine 10 pressure control valve assembly 20.
  • This includes a continuously adjustable control valve 21 with a zero coverage or small positive overlap between the control edges and with a pressure port 22, the fluidic with the pressure port 12 of the hydraulic machine 10 is connected to a tank connection 23 which is connected via the interior of the housing of the hydraulic machine 10 with a leak oil connection 30, and with a control connection 24 which is connected via a damping nozzle 25 with the adjusting chamber 19.
  • the valve piston of the control valve is in the sense of a connection of the control port 24 to the pressure port 22 and in the sense of reducing the stroke volume of the hydraulic machine 12 to negative values of the pump pressure and in the sense of connecting the control port 24 to the tank port 23 and in the sense of an increase of the stroke volume acted upon by a spring 26 and by a variable control pressure, which is tapped between a control oil 27 and a pressure-limiting valve 28 proportionally adjustable by an electromagnet 29, that is corresponds to the set value of the pressure relief valve.
  • the hydraulic motor 65 of the embodiment according to FIG. 3 is preferably one in axial piston construction, in particular in Schrägachsenbauweise, and as the hydraulic motor 15 of the embodiment according to FIG. 1 adjustable between a zero swallowing volume and a maximum swallowing volume. It is connected to the pressure line 14 with a pressure connection 76 and connected to the tank 9 via a tank connection 77. To change the absorption volume, the hydraulic motor 15 has an actuating piston 78, which is provided on one side with a piston rod 79 and thus a piston rod-side annular space 80 and a piston rod-side actuating chamber 81 from each other.
  • the inflow to and outflow of pressure fluid from the control chamber 81 is controlled by a torque control valve assembly 69 having a control valve 82 constructed on the hydraulic motor 65 and a pressure port 83 connected to the pressure port 76, a tank port 84 passing through the interior of the Housing of the hydraulic motor and a unspecified leakage connection with tank 9 is connected, and a control connection 85 which is connected to the actuating chamber 81.
  • the annulus 80 is permanently fluidly connected to the pressure port 76.
  • a control piston 82 of the control valve 82 is in the sense of a connection of the control connection 85 to the tank port 84 and in the sense of increasing the absorption volume of the hydraulic motor 65 by a spring 86 which is supported fixed to the housing, and acted upon via a control line 87 by a variable control pressure over the thus a remotely modifiable force can be exercised on the control piston.
  • the control pressure is maximum when the electrical system fails.
  • a connection of the control connection to the pressure port 83 of the control piston is acted upon by a force which depends on the position of the actuating piston 78 and thus the displacement of the hydraulic motor 65 and the pressure in the pressure line 14.
  • control racks are initially supported in a control position always the same distance from a housing-fixed axis of rotation of a lever 88 on this lever 88 from.
  • the lever 88 is acted upon by a rod 89 which is movably inserted into the adjusting piston 78 and at which the pressure prevails, which prevails in the pressure line 14.
  • the torque generated by the rod 89 on the lever 88 thus forms the product of the pressure applied to the hydraulic motor 65 and the displacement of the hydraulic motor and thus the output torque of the hydraulic motor.
  • An opposite torque on the lever 88 generates the sum of the forces exerted by the spring 86 and the control pressure on the control piston of the control valve 82.
  • the sum of the torques acting on the lever 88 must be zero. If, for example, the pressure in the pressure line 14 increases, the torque exerted on the lever 88 via the rod 89 becomes greater than the torque exerted via the control piston.
  • the lever is rotated and displaced the control piston, so that the control port 85 is connected to the pressure port 83 of the control valve 82.
  • the actuating chamber 81 flows to pressure medium and the adjusting piston moves in the direction of reduction of the absorption volume. With the actuating piston, the rod 89 moves along the lever 88, so that the lever arm for the pressure force acting on the rod is smaller, until an equilibrium between the torques again exists.
  • the control pressure in the control line 87 does not change, the torque exerted by the hydraulic motor 65 does not change when the pressure level in the pressure line 14 changes. Conversely, by changing the control pressure, the torque and thus the fan speed can be changed.
  • FIG. 3 is as in the embodiment after FIG. 2 provided that 10 independent of the hydraulic pump pressure medium can be fed into the hydraulic fan circuit.
  • the hydraulic accumulator 17 makes it possible for the amount fed in to be greater than the quantity currently swallowed by the hydraulic motor 65, without the excess amount being hosed off via a pressure-limiting valve.
  • FIG. 3 is shown the supply of pressure medium in the pressure line and in the hydraulic accumulator 17 in the lowering of a load, which is indicated here by a hydraulic cylinder 95.
  • a flow control valve 96 is provided with a proportionally adjustable metering orifice (not shown in detail) and a pressure compensator arranged serially thereto.
  • a check valve 97 blocking the flow control valve.
  • a 2/2 way valve 98 is connected to open a flow to the tank can.
  • Displaced from the hydraulic cylinder pressure medium can be fed at the desired lowering rate in the pressure line 14 when the load pressure to the pressure drop across the orifice of the flow control valve 96 is higher than the pressure in the pressure line 14 and the hydraulic accumulator 17. It may be that this The beginning of a lowering is given, but not in the further course, since the pressure in the hydraulic accumulator 17 increases. Then the valve 98 must be opened. Whether it is still possible to feed in can be done with the help of pressure sensors; which detect the load pressure and the accumulator pressure, determine. It is also possible to monitor the position of the pressure compensator. When the pressure compensator is fully open, feed-in is no longer possible.
  • the additional amount of pressure medium fed in With regard to the additional amount of pressure medium fed in, one can distinguish two cases. If the quantity of pressure medium fed in is smaller than the consumption by the hydraulic motor 65, the remaining quantity is conveyed by the hydraulic pump 60 and the pressure level in the system remains at the level set at the hydraulic pump 60. Also in this case, an energy saving is achieved because the hydraulic pump 60 pivots to a smaller displacement.
  • the pressure in the fan circuit rises above the level set at the hydraulic pump 60.
  • the hydraulic pump is back-regulated by pressure cut to zero stroke, in which case a swing angle sensor could be used here, with which the pivoting angle is scanned.
  • the valve 28 would then each be adjusted so that the pivot angle is zero or just above zero.
  • the pressure level can now assume a much higher value, for example 300 bar, until it is limited by a pressure limiting valve 99 connected to the pressure line 14. If nothing is more or only fed less than the hydraulic motor 65 consumed, so first takes over the hydraulic accumulator 17, the full or partial supply of the fan circuit until at a pressure level of 100 bar, the hydraulic pump 60 swings out again.
  • a suction valve 100 opening from the tank port to the pressure port 76 is arranged.
  • an electronic control of the output torque of the hydraulic motor 65 conceivable, wherein the accumulator pressure detected by a sensor and the displacement is adjusted according to the required torque.
  • a foreign energy source for example a lifting cylinder in a lowering process or an additional hydraulic pump, can be used to drive the fan wheel.
  • a short-term support of the diesel engine is possible via the hydraulic machine 10.
  • a hydromotor in particular in a fan drive with an EP adjustment of the hydraulic motor according to the embodiment according to FIG. 1 or an electrical adjustment with swivel angle feedback by means of an electrical swivel angle sensor, a hydromotor can be used which can be swiveled over zero. Then you can reverse the direction of rotation of the fan without additional valve to blow the radiator clean. This is particularly advantageous for forestry and construction machinery.

Claims (10)

  1. Entraînement hydraulique de ventilateur comprenant une pompe hydraulique (10, 60) de cylindrée réglable, à laquelle est associé un agencement de soupape de régulation de pression (20, 70) pour la régulation d'une pression de pompe par réglage de la cylindrée, comprenant un moteur hydraulique (15, 65) pour l'entraînement d'une roue de ventilateur (16) et comprenant une conduite de pression (14) qui est raccordée à un raccord de pression (35, 76) du moteur hydraulique (15, 65) et dans laquelle un fluide sous pression peut être refoulé par la pompe hydraulique (10, 60), caractérisé en ce qu'un accumulateur hydraulique (17) est notamment raccordé directement à la conduite de pression (14) et le volume d'absorption du moteur hydraulique (15, 65) peut être réglé.
  2. Entraînement hydraulique de ventilateur selon la revendication 1, caractérisé en ce que l'ajustement de l'agencement de soupape de régulation de pression (20) peut être modifié par commande à distance.
  3. Entraînement hydraulique de ventilateur selon la revendication 1 ou 2, caractérisé en ce qu'entre la pompe hydraulique (60) et une section de la conduite de pression (14) à laquelle est raccordé l'accumulateur hydraulique (17), est disposé un clapet antiretour (66) qui se ferme en direction de la pompe hydraulique (60).
  4. Entraînement hydraulique de ventilateur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'une conduite de branchement (94) débouche dans la conduite de pression (14), par le biais de laquelle du fluide sous pression peut être injecté dans la conduite de pression (14) indépendamment de la pompe hydraulique (60).
  5. Entraînement hydraulique de ventilateur selon les revendications 3 et 4, caractérisé en ce qu'un clapet antiretour (97) se trouve dans la conduite de branchement (94), lequel s'ouvre vers la section de la conduite de pression (14).
  6. Entraînement hydraulique de ventilateur selon l'une quelconque des revendications précédentes, caractérisé en ce que la pompe hydraulique (10) peut aussi fonctionner en tant que moteur hydraulique en conservant le sens de rotation.
  7. Entraînement hydraulique de ventilateur selon la revendication 6, caractérisé en ce que la pompe hydraulique (10) est une pompe hydraulique réglable par passage par zéro, de sorte qu'elle puisse également fonctionner en tant que moteur hydraulique avec le même raccord de pression (12) et le même sens de rotation.
  8. Entraînement hydraulique de ventilateur selon l'une quelconque des revendications précédentes, caractérisé en ce qu'au moteur hydraulique (15, 65) est associé un agencement de soupape de régulation de couple (69) pour régler un couple du moteur par réglage du volume d'absorption.
  9. Entraînement hydraulique de ventilateur selon la revendication 8, caractérisé en ce que l'agencement de soupape de régulation de couple (69) présente un piston de soupape qui est sollicité dans le sens d'une augmentation du volume d'absorption du moteur hydraulique (65) par une force variable commandée à distance et qui est supporté sur un levier (88) à une distance au moins approximativement fixe d'un axe de rotation, et en ce que dans le sens opposé, une force de pression dépendant de la pression dans la conduite de pression (14) et agissant sur le piston de soupape dans le sens d'une réduction du volume d'absorption s'exerce sur le levier (88), la distance du point d'introduction de la force de pression dans le levier (88) à son axe de rotation dépendant de la position d'un piston de commande (78) du moteur hydraulique (65) et donc du volume d'absorption du moteur hydraulique (65).
  10. Entraînement hydraulique de ventilateur selon l'une quelconque des revendications 1 à 7, caractérisé en ce qu'au moteur hydraulique (65) est associé un agencement de soupape de régulation (42), avec lequel le volume d'absorption du moteur hydraulique (15) peut être modifié de manière proportionnelle à un signal de commande, le signal de commande dépendant d'une part d'une valeur de consigne de régime du moteur hydraulique (15) et d'autre part d'un régime détecté du moteur hydraulique (15) ou de la pression détectée dans la conduite de pression (14) et dans l'accumulateur hydraulique (17).
EP11718903.5A 2010-03-30 2011-03-03 Entraînement hydraulique de ventilateur Not-in-force EP2553231B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102010013453 2010-03-30
PCT/DE2011/000217 WO2011120486A2 (fr) 2010-03-30 2011-03-03 Entraînement hydraulique de ventilateur

Publications (2)

Publication Number Publication Date
EP2553231A2 EP2553231A2 (fr) 2013-02-06
EP2553231B1 true EP2553231B1 (fr) 2014-01-01

Family

ID=44626290

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11718903.5A Not-in-force EP2553231B1 (fr) 2010-03-30 2011-03-03 Entraînement hydraulique de ventilateur

Country Status (7)

Country Link
US (1) US20130202452A1 (fr)
EP (1) EP2553231B1 (fr)
JP (1) JP5599504B2 (fr)
KR (1) KR20130018253A (fr)
CN (1) CN102812218B (fr)
DE (1) DE102011012905A1 (fr)
WO (1) WO2011120486A2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105971053A (zh) * 2016-06-30 2016-09-28 徐州徐工挖掘机械有限公司 一种挖掘机节能系统

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011011888A1 (de) * 2011-02-21 2012-08-23 Robert Bosch Gmbh Hydraulischer Lüfterantrieb
US8984872B2 (en) * 2011-07-08 2015-03-24 Caterpillar Inc. Hydraulic accumulator fluid charge estimation system and method
DE102012003320A1 (de) * 2012-02-18 2013-08-22 Robert Bosch Gmbh Mobile Arbeitsmaschine mit Energierückgewinnung zum Antrieb der Motorkühlung
DE102012101806A1 (de) * 2012-03-05 2013-09-05 Claas Selbstfahrende Erntemaschinen Gmbh Hydrauliksystem für eine selbstfahrende Arbeitsmaschine
DE102012014250A1 (de) 2012-07-19 2014-01-23 Hydac System Gmbh Ventil, insbesondere Stetigventil
CN102996455B (zh) * 2012-12-06 2015-05-06 无锡压缩机股份有限公司 喷油螺杆压缩机润滑油压能量回收系统
CN102975112B (zh) * 2012-12-24 2015-08-05 厦门大学 一种在线可控抛光装置
DE102013224113A1 (de) 2013-11-26 2015-05-28 Robert Bosch Gmbh Hydromotor
DE102013224112B4 (de) 2013-11-26 2024-01-18 Robert Bosch Gmbh Hydromaschine in Axialkolbenbauweise mit einer durch einen Proportionalmagneten verstellbaren Schrägscheiben-Stelleinrichtung
DE102014218419A1 (de) * 2014-09-15 2016-03-17 Robert Bosch Gmbh Hydrostatischer Antrieb
GB201602710D0 (en) * 2016-02-16 2016-03-30 Rolls Royce Cabin blower system
CN105650044A (zh) * 2016-03-15 2016-06-08 雷沃重工股份有限公司 收获机用紧急制动系统及其制动方法
CN108194388A (zh) * 2016-05-04 2018-06-22 何春晖 一种风扇
CN106013315B (zh) * 2016-06-30 2018-02-13 徐州徐工挖掘机械有限公司 一种挖掘机回收能量利用系统
US10330126B2 (en) * 2016-12-16 2019-06-25 Caterpillar Inc. Fan control system with electro-hydraulic valve providing three fan motor operational positions
DE102017011905A1 (de) * 2017-12-21 2019-06-27 Wabco Gmbh Verfahren und Einrichtung zum Betreiben eines pneumatischen Systems mit einer Druckluftversorgungsanlage und einer Luftfederanlage und pneumatisches System mit einer Druckluftversorgungsanlage und einer Luftfederanlage sowie Fahrzeug
CN108644001B (zh) * 2018-07-13 2024-02-09 安徽合力股份有限公司 一种液压马达驱动的智能散热系统及其散热方法
DE102019215885A1 (de) * 2019-10-16 2021-04-22 Robert Bosch Gmbh Verstelleinrichtung und Hydromaschine
DE102020200958A1 (de) 2020-01-28 2021-07-29 Robert Bosch Gesellschaft mit beschränkter Haftung Hydraulisches Antriebssystem mit nach unten begrenztem Förderdruck der Pumpe
CN112942480B (zh) * 2021-01-29 2022-05-24 徐州徐工挖掘机械有限公司 混合动力工程机械液压系统以及混合动力工程机械
CN113847297A (zh) * 2021-10-19 2021-12-28 徐工消防安全装备有限公司 一种电负载敏感系统及其控制方法

Family Cites Families (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1262678B (de) * 1962-07-18 1968-03-07 Sueddeutsche Kuehler Behr Regelbarer hydraulischer Antrieb fuer den Luefter der Kuehlanlage einer Brennkraftmaschine
US3902566A (en) * 1971-11-05 1975-09-02 James M Bird Hydraulic drive system for vehicle
JPH02127803U (fr) * 1989-03-30 1990-10-22
US5168703A (en) * 1989-07-18 1992-12-08 Jaromir Tobias Continuously active pressure accumulator power transfer system
DE4001306A1 (de) * 1990-01-18 1991-07-25 Bosch Gmbh Robert Hydraulikanlage fuer ein kraftfahrzeug
JP2778316B2 (ja) * 1991-11-29 1998-07-23 日産自動車株式会社 車両用補機駆動装置
DE4321637A1 (de) 1993-06-30 1995-01-12 Rexroth Mannesmann Gmbh Hydraulischer Antrieb, insbesondere hydraulischer Lüfterantrieb für die Kühlanlage einer Brennkraftmaschine
US5531190A (en) * 1994-12-09 1996-07-02 Sauer Inc. Electrohydraulic fan control
JP3856404B2 (ja) * 1996-12-10 2006-12-13 株式会社小松製作所 建設機械の冷却装置
JP2000130164A (ja) * 1998-10-26 2000-05-09 Komatsu Ltd 冷却用ファンの駆動装置
US6311488B1 (en) * 1998-10-26 2001-11-06 Komatsu Ltd. Cooling fan drive apparatus
JP4204137B2 (ja) * 1999-04-22 2009-01-07 株式会社小松製作所 冷却用ファンの駆動制御装置
US20010024618A1 (en) * 1999-12-01 2001-09-27 Winmill Len F. Adjustable-displacement gear pump
JP4261024B2 (ja) * 2000-05-17 2009-04-30 株式会社小松製作所 シルティング防止制御装置
JP3794960B2 (ja) * 2001-03-15 2006-07-12 ナブテスコ株式会社 流体モータの駆動回路
US6655136B2 (en) * 2001-12-21 2003-12-02 Caterpillar Inc System and method for accumulating hydraulic fluid
US6681568B2 (en) * 2002-03-28 2004-01-27 Caterpillar Inc Fluid system for two hydraulic circuits having a common source of pressurized fluid
US7273122B2 (en) * 2004-09-30 2007-09-25 Bosch Rexroth Corporation Hybrid hydraulic drive system with engine integrated hydraulic machine
JP4628816B2 (ja) * 2005-02-18 2011-02-09 株式会社小松製作所 油圧駆動機械におけるエネルギー回生装置

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105971053A (zh) * 2016-06-30 2016-09-28 徐州徐工挖掘机械有限公司 一种挖掘机节能系统

Also Published As

Publication number Publication date
US20130202452A1 (en) 2013-08-08
JP2013524107A (ja) 2013-06-17
CN102812218B (zh) 2015-07-22
CN102812218A (zh) 2012-12-05
WO2011120486A3 (fr) 2012-01-05
DE102011012905A1 (de) 2011-10-06
WO2011120486A2 (fr) 2011-10-06
EP2553231A2 (fr) 2013-02-06
KR20130018253A (ko) 2013-02-20
JP5599504B2 (ja) 2014-10-01

Similar Documents

Publication Publication Date Title
EP2553231B1 (fr) Entraînement hydraulique de ventilateur
EP3177823B1 (fr) Arrangement avec un entraînement hydrostatique
DE102010053105B4 (de) Hydrostatischer Antrieb
EP2542779B1 (fr) Dispositif de régulation et méthode de commande de couple d'un 'arbre de commande d'un moteur pour machine hydrostatique
EP2628862B1 (fr) Machine de travail mobile avec production d'énergie pour l'entraînement du refroidissement du moteur
DE19538649A1 (de) Leistungsregelung mit Load-Sensing
EP3194758B1 (fr) Entraînement hydrostatique
EP2029408B1 (fr) Entraînement à fonction de récupération d'énergie avec soupape de régulation de pression de freinage
DE102010054100A1 (de) Hydraulisches System
WO2018177640A1 (fr) Dispositif de régulation d'une machine hydraulique
DE102010014071B4 (de) Hydraulische Anlage
EP2655895B1 (fr) Entraînement hydraulique
DE102017003963A1 (de) Hydraulische, insbesondere druckspeicherlose, Antriebsanordnung für und mit einem Verbraucher, insbesondere für Pressen, sowie Verfahren zum Betreiben einer hydraulischen Antriebsanordnung
WO2013083234A1 (fr) Système d'entraînement hydrostatique
DE102011113542A1 (de) Hydraulischer Lüfterantrieb für einen Verbrennungsmotor
WO2012041497A2 (fr) Entraînement hydrostatique
EP2682610B1 (fr) Système de réglage d'une pompe hydraulique à débit variable
DE102017202273A1 (de) Hydrostatisches Getriebe und Verfahren zur Bremsung damit
DE102012012977A1 (de) Hydraulischer Antrieb
WO2012038050A1 (fr) Machine hydraulique comportant des soupapes à commande électronique
DE102020208756A1 (de) Hydraulisches System, Verfahren und Verwendung des hydraulischen Systems
DE102010020528A1 (de) Hydrostatischer Antrieb
DE3812312A1 (de) Hydraulischer antrieb fuer einen gurtbandfoerderer
DE102012015017A1 (de) Hydrostatischer Antrieb
WO2012113512A2 (fr) Entraînement hydraulique de ventilateur

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: 20121030

AK Designated contracting states

Kind code of ref document: A2

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

DAX Request for extension of the european patent (deleted)
GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20131014

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: 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: AT

Ref legal event code: REF

Ref document number: 647712

Country of ref document: AT

Kind code of ref document: T

Effective date: 20140215

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502011001945

Country of ref document: DE

Effective date: 20140220

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20140101

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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

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: 20140101

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: 20140501

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: 20140101

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: 20140101

Ref country code: SE

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: 20140101

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: 20140101

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: 20140101

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: 20140502

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

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: 20140101

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: 20140101

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: 20140101

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011001945

Country of ref document: DE

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

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: 20140101

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: 20140101

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: 20140101

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: 20140101

Ref country code: LU

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: 20140303

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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: 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: 20140101

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: 20140101

26N No opposition filed

Effective date: 20141002

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20141128

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502011001945

Country of ref document: DE

Effective date: 20141002

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

Ref country code: CH

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

Effective date: 20140331

Ref country code: IE

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

Effective date: 20140303

Ref country code: LI

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

Effective date: 20140331

Ref country code: FR

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

Effective date: 20140331

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: 20140101

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

Effective date: 20150303

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: 20150303

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

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: 20140101

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: 20140101

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: 20140401

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: 20140101

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: 20140101

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: 20140402

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20140331

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: 20110303

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: 20140101

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 647712

Country of ref document: AT

Kind code of ref document: T

Effective date: 20160303

REG Reference to a national code

Ref country code: DE

Ref legal event code: R084

Ref document number: 502011001945

Country of ref document: DE

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: 20160303

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

Ref country code: IT

Payment date: 20170323

Year of fee payment: 7

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

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: 20140101

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: 20140101

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: 20180303

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

Ref country code: DE

Payment date: 20200526

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502011001945

Country of ref document: DE

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

Ref country code: DE

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

Effective date: 20211001