EP3054161A1 - Method for operating a gear wheel pump and gear wheel pump - Google Patents
Method for operating a gear wheel pump and gear wheel pump Download PDFInfo
- Publication number
- EP3054161A1 EP3054161A1 EP15002727.4A EP15002727A EP3054161A1 EP 3054161 A1 EP3054161 A1 EP 3054161A1 EP 15002727 A EP15002727 A EP 15002727A EP 3054161 A1 EP3054161 A1 EP 3054161A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- gear
- gears
- housing
- gear pump
- relative
- 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
Links
- 238000000034 method Methods 0.000 title claims abstract description 17
- 239000003921 oil Substances 0.000 claims abstract description 23
- 239000007788 liquid Substances 0.000 claims abstract description 22
- 239000010705 motor oil Substances 0.000 claims abstract description 4
- 238000006073 displacement reaction Methods 0.000 claims description 12
- 238000002485 combustion reaction Methods 0.000 claims description 9
- 238000010276 construction Methods 0.000 claims description 5
- 230000010349 pulsation Effects 0.000 description 7
- 238000011161 development Methods 0.000 description 3
- 230000018109 developmental process Effects 0.000 description 3
- 239000012530 fluid Substances 0.000 description 3
- 230000000694 effects Effects 0.000 description 2
- 239000003795 chemical substances by application Substances 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
- F04C11/001—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of similar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/02—Pressure lubrication using lubricating pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C14/00—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations
- F04C14/18—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber
- F04C14/22—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by varying the volume of the working chamber by changing the eccentricity between cooperating members
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/084—Toothed wheels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
- F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/02—Pressure lubrication using lubricating pumps
- F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
- F01M2001/0238—Rotary pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01M—LUBRICATING OF MACHINES OR ENGINES IN GENERAL; LUBRICATING INTERNAL COMBUSTION ENGINES; CRANKCASE VENTILATING
- F01M1/00—Pressure lubrication
- F01M1/02—Pressure lubrication using lubricating pumps
- F01M2001/0207—Pressure lubrication using lubricating pumps characterised by the type of pump
- F01M2001/0246—Adjustable pumps
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/18—Pressure
Definitions
- the invention relates to a method for operating a gear pump according to the preamble of claim 1, a gear pump according to the preamble of claim 6 and a vehicle, in particular a commercial vehicle, and / or an internal combustion engine for carrying out the method and / or with the gear pump according to claim 18th ,
- the gear pump may be formed, for example, as an internal gear pump, wherein at least one externally toothed gear meshing with at least one internally toothed gear.
- Such an internal gear pump is usually driven by the internal gear.
- a gear pump as an external gear pump in which at least one externally toothed gear meshes with at least one further externally toothed gear.
- the external gear pump is driven by means of at least one of these externally toothed gears.
- the promotion of the oil or the liquid to be delivered takes place by means of the tooth spaces between the individual teeth of the gears. These tooth gaps form delivery chambers, by means of which the liquid to be conveyed is conveyed in the direction of rotation of the respective toothed wheel.
- a gear machine with an engine made of at least two gear paths the gears are guided with their hubs on at least two rotatably mounted in the housing shafts.
- the driven gears of the at least two pairs of gears are arranged together on one of the shafts and rotatably coupled via a trained on this one shaft outer teeth and formed in the hubs of the driven gears internal teeth with this one shaft.
- the outer toothing of the shaft here consists of at least two toothed parts which are spaced from one another and have a tooth offset with one another and are each associated with one of the driven toothed wheels. In this way, it is ensured simply and reliably that the gears are set at their assembly by half Zahnteilu ng offset from each other on the common shaft.
- a method for operating a gear pump in particular for the promotion of oil in an oil circuit of a vehicle, proposed, wherein a conveyor with at least two arranged in a housing, in particular externally toothed or formed as a spur gears, is provided, by means of the gears a liquid to be pumped can be promoted starting from at least one housing inlet to at least one housing outlet, and wherein the gears, as seen in the axial direction, are arranged one behind the other.
- an adjusting device is provided by means of which the gears are rotated relative to one another and / or displaced relative to one another as a function of the pressure conditions in the interior of the housing, in particular as a function of the suction vacuum at the housing inlet and / or as a function of the liquid back pressure at the housing outlet.
- the operation of the gear pump is optimized in a simple and effective manner, since the gears are now rotated in dependence on the pressure conditions in the interior of the housing relative to each other and / or displaced relative to each other.
- About the pressure conditions inside the housing can be reliably detected, whether currently a particularly high suction force of the gear pump and thus a particularly high flow rate of the gear pump is required or not.
- the gears can then for example be rotated relative to each other and / or relocated relative to each other, that the capacity of the gear pump is particularly high or the amplitudes of the pressure pulsations of the gear pump are as low as possible.
- the gears can also be displaced in intermediate positions, which ensure a sufficient flow rate and simultaneously reduced amplitudes of the pressure pulsations.
- the gears can, viewed in the axial direction, be spaced from each other with a defined gap spacing in the housing. However, it is preferred if the successively arranged toothed wheels are in contact with one another in order to realize a particularly compact construction.
- the gears are arranged in the housing such that their axes of rotation are substantially congruent or aligned parallel to each other to form the gear pump particularly simple and effective. More preferably, the gears are axially rotated by means of the adjusting device in dependence on the pressure conditions in the interior of the housing relative to each other and / or displaced relative to each other in the radial direction.
- the absorbency and the amplitudes of the pressure pulsations of the gear pump can be easily and effectively adjusted or adjusted.
- the gears have a substantially identical radial outer contour.
- the gears are then arranged in a basic position, seen in the axial direction, aligned with each other. If the liquid back pressure at the housing outlet falls below at least a defined minimum value, the gears are shifted from a position not corresponding to the basic position by means of the adjusting device into the basic position. In this basic position, the suction capacity or the suction force of the gear pump is greatest. By the displacement of the gears in the basic position is thus reliably ensured that the capacity of the gear pump is maximum.
- this basic position of the gears for example, at a start of an internal combustion engine of the vehicle advantageous because the oil pressure is built up so quickly and air bubbles are degraded quickly.
- the liquid back pressure at the housing outlet is particularly low.
- the basic position in an oil circuit of a vehicle at low speeds of the gear pump and high oil temperatures is advantageous, since despite the low viscosity oil so-called gap losses is better compensated by the flow of oil between the delivery chambers and in the bearing points of the pump and the internal combustion engine. In this operating situation, the liquid back pressure at the housing outlet is also very low.
- the gears arranged in the basic position are rotated relative to one another by means of the adjusting device and / or displaced relative to one another. In this way, the amplitudes of the pressure pulsations are reduced when the maximum suction or suction force of the gear pump is not needed.
- the toothed wheels are preferably displaced into a maximum position in which the toothed wheels are arranged rotated by half a tooth pitch relative to one another. In this maximum position, the amplitudes of the pressure pulsations are particularly low.
- the fluid back pressure at the housing outlet is usually particularly high in an oil circuit of a vehicle at higher speeds of the gear pump.
- a gear pump in particular for the promotion of oil in an oil circuit of a vehicle, proposed with a conveyor having at least two arranged in a housing, in particular externally toothed and / or formed as spur gears, gears, by means of A fluid to be conveyed can be conveyed from the toothed wheels starting from at least one housing inlet to at least one housing outlet, and wherein the toothed wheels, viewed in the axial direction, are arranged one behind the other, in particular with a defined gap distance.
- an adjusting device is provided by means of which the gears can be rotated relative to one another and / or displaced relative to one another in dependence on the pressure conditions in the interior of the housing, in particular as a function of the suction vacuum at the housing inlet and / or as a function of the liquid back pressure at the housing outlet.
- a fixing device is provided, by means of which at least one, a setting gear forming gear relative to at least one other gear is displaceable and / or rotatably fixed to the housing.
- the gears can be particularly easily rotated relative to each other and / or displaced relative to each other.
- the adjusting device has at least one biasing element, by means of which the adjusting gear can be biased into a basic position.
- the biasing element is formed by a spring element, in particular by a torsion spring, in order to make the biasing element functionally reliable and simple.
- the biasing member cooperates with a stop, in particular with at least one stop element, which prevents rotation and / or displacement of the arranged in the basic position adjusting gear in at least one defined direction. So can an unwanted twisting and / or displacement of the adjusting gear in at least one defined direction can be reliably prevented.
- a stop element is provided by means of which the displacement and / or rotation of the arranged in the basic position adjusting gear can be limited to a defined extent. In this way it is reliably and easily ensured that the adjusting gear can move only in a defined degree relative to the at least one other gear.
- the gear pump may be formed, for example, as an internal gear pump, wherein the at least two gears are formed by externally toothed gears, which are in meshing engagement with at least one internally toothed gear member.
- the internally toothed gear element or an externally toothed gear element which does not form an adjusting gear, forms a drive gear for driving the internal gear pump in order to be able to drive the gear pump particularly easily.
- the fixing device has a fixing element, by means of which the adjusting gear is fixed relative to the housing displaceable on the housing, wherein the adjusting gear is rotatably fixed to form a first axis of rotation on the fixing element, wherein the fixing element to form a substantially arranged parallel to the first axis of rotation, the second axis of rotation is rotatably attached to the housing, and wherein the adjusting gear can be displaced by rotation of the fixing element relative to the housing.
- the fixing element is formed substantially Z-shaped to form the fixing function optimized.
- the biasing element is tensioned by rotating the fixing in a first direction of rotation.
- the biasing element is then relaxed by rotating the fixing in a direction opposite to the first direction of rotation, the second direction of rotation.
- the adjusting gear can be particularly easily biased by the biasing member in the basic position.
- the biasing element is fixed with an end portion on a protruding from the housing portion of the fixing element in order to fasten the biasing member in a particularly simple manner to the fixing element can.
- the gear pump may also be formed as an external gear pump, wherein the at least two gears are formed by externally toothed gears and drive gears to drive the external gear pump, and wherein each of these drive gears is in meshing engagement with a corresponding externally toothed gear.
- the fixing device has a rotatably fixed to the housing drive shaft for driving the drive gears, wherein at least one drive gear rotatably connected to the drive shaft, wherein at least one, the adjusting gear forming drive gear is fixed relative to the drive shaft axially rotatable on the drive shaft, and wherein the drive shaft is connected by means of the biasing element to transmit torque to the adjusting gear.
- the adjusting gear can be particularly easily set rotatable relative to the other gear.
- the biasing member is biased by rotating the adjusting gear relative to the drive shaft in a first direction of rotation.
- the biasing member is then relaxed by turning the adjusting gear relative to the drive shaft in a direction opposite to the first rotational direction, second rotational direction.
- the adjusting gear can also be biased particularly easy by means of the biasing member in the basic position.
- the biasing element, in Seen axially, between the drive gears is arranged to realize a particularly compact design.
- the biasing element can also be arranged between the adjusting gear and a housing wall or protrude out of the housing.
- a vehicle in particular a commercial vehicle, and / or an internal combustion engine for carrying out the method according to the invention and / or claimed with the gear pump according to the invention.
- the resulting advantages are identical to the already acknowledged advantages of the method according to the invention and / or the gear pump according to the invention, so that they are not repeated at this point.
- the internal combustion engine can be designed, for example, as a stationary internal combustion engine or as a marine internal combustion engine.
- Fig. 1 is an example here designed as internal gear pump 1 gear pump shown.
- the internal gear pump 1 has a housing 3, which in Fig. 1 is shown open.
- the housing 3 here has a housing inlet 5 and a housing outlet 7.
- the internal gear pump 1 can be connected, for example, to an oil circuit of a vehicle so that the oil to be conveyed by means of the internal gear pump 1 reaches the interior of the housing 3 via the housing inlet 5 and out of the housing via the housing outlet 7 3 exit.
- the internal gear pump 1 has a arranged inside the housing 3 internally toothed, here exemplified as a spur gear 9, which forms a drive gear for driving the internal gear pump 1.
- the internally toothed spur gear 9 is in meshing engagement with a plurality of gears, here by way of example with two externally toothed gears, likewise designed as spur gears 11, 13.
- the externally toothed spur gears 11, 13 are here for example identical or identical in construction and, in the axial direction x ( Fig. 3 ), arranged one behind the other in the housing 3 with a defined gap distance.
- the internally toothed spur gear 9 is rotationally driven by means of a suitable drive device not shown in the figures.
- the externally toothed spur gear 13 is fixed here by way of example on an axis 19 axially rotatable.
- the axis 19 is here by way of example rigid or immobile fixed to the housing 3.
- the externally toothed spur gear 11 is here by way of example by means of an actuating device 21 (FIG. Fig. 3 ) relative to the externally toothed spur gear 13 displaceable and rotatably fixed to the housing 3.
- the externally toothed spur gear 11 can by means of the adjusting device 21, for example in an in Fig. 2 are shown, in which the externally toothed spur gears 11, 13, seen in the axial direction x or in plan view, are aligned with each other.
- the externally toothed spur gear 11 can be arranged here by way of example also in a maximum position, in which the externally toothed spur gears 11, 13 are arranged rotated by half a tooth pitch relative to each other.
- the externally toothed spur gear 11 is arranged in a position between the basic position and the maximum position.
- the axes of rotation of the spur gears 11, 13 are here, for example, then aligned parallel to each other.
- the adjusting device 21 has a fixing device 23, by means of which, the adjusting gear forming a gear wheel 11 is fixed relative to the housing 3 and thus also to the spur gear 13 displaceable or rotatable on the housing 3.
- the fixing device 23 here comprises an essentially Z-shaped fixing element 25 which has an axis 27 forming a first axis of rotation A 1 on which the adjusting gear 11 is fixed in an axially rotatable manner.
- the fixing element 25 also has a second axis of rotation A 2 forming axis 29, by means of which the fixing element 25 is rotatably fixed to the housing 3.
- the axes 27, 29 are offset from one another in such a way that the second axis of rotation A 2 is arranged parallel to the first axis of rotation A 1 .
- the adjusting device 21 further also has a preloading element embodied here by way of example as a torsion spring 31, by means of which the adjusting gearwheel 11 is moved into the basic position (FIG. Fig. 2 ) is biased.
- the torsion spring 31 is here exemplified by rotating the fixing element 25 in a first direction of rotation R 1 (FIG. Fig. 4 ) stretched around the second axis of rotation A 2 .
- R 1 first direction of rotation
- R 2 opposite to the first direction of rotation
- the torsion spring 31 is here by way of example with an end region 33 on a protruding from the housing 3 End region 35 of the fixing element 25 and fixed to a second end portion 37 fixed or rigid at a vehicle-side fixing point 39.
- the actuator 25 is here for example by means of the torsion spring 31 against a in Fig. 4 biased stop member 41 biased.
- the stop element 41 prevents a rotation and / or displacement of the arranged in the basic position adjusting gear 11 in the first direction of rotation R 2nd
- the torsion spring 31 is here exemplarily designed such that the fixing element 25 rotates at defined pressure conditions in the housing 3 in the first direction of rotation R 1 . By this rotation, the torsion spring 31 is tensioned to build up a restoring force.
- the actuating device 21 also has a stop element 43 by means of which the rotation of the fixing element 25 in the first direction of rotation R 1 and thus also the displacement or rotation of the adjusting gear 11 from the basic position is limited such that the actuating element Gear 11 can only be moved to the maximum position.
- the gear pump is exemplified here as external gear pump 45.
- the external gear pump 45 has a plurality of, here exemplified two, here as spur gears 47, 49 formed externally toothed drive gears for driving the external gear pump 45.
- Each of these spur gears 47, 49 is here exemplarily in meshing engagement with a corresponding, here also designed as a spur gear 51.
- the spur gears 51 are set here by way of example on an axis 52 axially rotatable.
- the axis 52 is fixed here by way of example rigidly or immovably to the housing 3.
- the spur gears 47, 49, 51 are identical or identical in construction.
- the fixing device 23 here has a rotatably fixed to the housing 3 drive shaft 53 for driving the spur gears 47, 49.
- the spur gear 47 is here exemplified rotatably connected to the drive shaft 53.
- the spur gear 49 forming an adjusting gearwheel is fixed here in an axially rotatable manner on the drive shaft 53 relative to the drive shaft 53.
- the two spur gears 47, 49 are here connected in a torque-transmitting manner by means of a pretensioning element designed as a torsion spring 55.
- the torsion spring 55 is exemplary here, in the axial direction x seen between the spur gears 47, 49 arranged.
- the torsion spring 55 is tensioned by turning the adjusting gear 49 relative to the drive shaft 53 and thus also relative to the gear 47 in a first rotational direction. In addition, the torsion spring 55 is relaxed by turning the adjusting gear 49 relative to the drive shaft 53 in a direction opposite to the first rotational direction of the second rotational direction.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
- Details And Applications Of Rotary Liquid Pumps (AREA)
Abstract
Die Erfindung betrifft ein Verfahren zum Betreiben einer Zahnradpumpe, insbesondere zur Förderung von Motoröl in einem Ölkreislauf eines Fahrzeugs, wobei eine Fördereinrichtung mit wenigstens zwei in einem Gehäuse (3) angeordneten, insbesondere außenverzahnten und/oder als Stirnräder ausgebildeten, Zahnrädern (11, 13, 47, 49) vorgesehen ist, wobei mittels der Zahnräder (11, 13, 47, 49) eine zu fördernde Flüssigkeit ausgehend von wenigstens einem Gehäuseeinlass (5) hin zu wenigstens einem Gehäuseauslass (7) föderbar ist, und wobei die Zahnräder (11, 13, 47, 49), in Axialrichtung (x) gesehen, hintereinander angeordnet sind. Erfindungsgemäß ist eine Stelleinrichtung (21) vorgesehen, mittels der die Zahnräder (11, 13, 47, 49) in Abhängigkeit von den Druckverhältnissen im Inneren des Gehäuses (3), insbesondere in Abhängigkeit vom Saugunterdruck am Gehäuseeinlass (5) und/oder in Abhängigkeit vom Flüssigkeitsgegendruck am Gehäuseauslass (7), relativ zueinander verdreht und/oder relativ zueinander verlagert werden.The invention relates to a method for operating a gear pump, in particular for conveying engine oil in an oil circuit of a vehicle, wherein a conveyor with at least two in a housing (3) arranged, in particular externally toothed and / or formed as spur gears, gears (11, 13, 47, 49) is provided, wherein by means of the gears (11, 13, 47, 49) a liquid to be conveyed starting from at least one housing inlet (5) towards at least one housing outlet (7) is föderbar, and wherein the gears (11, 13, 47, 49), viewed in the axial direction (x), are arranged one behind the other. According to the invention an adjusting device (21) is provided, by means of which the gears (11, 13, 47, 49) in dependence on the pressure conditions in the interior of the housing (3), in particular depending on the suction vacuum at the housing inlet (5) and / or in dependence be rotated by the liquid back pressure at the housing outlet (7) relative to each other and / or displaced relative to each other.
Description
Die Erfindung betrifft ein Verfahren zum Betreiben einer Zahnradpumpe nach dem Oberbegriff des Patentanspruches 1, eine Zahnradpumpe nach dem Oberbegriff des Patentanspruches 6 sowie ein Fahrzeug, insbesondere ein Nutzfahrzeug, und/oder eine Brennkraftmaschine zur Durchführung des Verfahrens und/oder mit der Zahnradpumpe nach Patentanspruch 18.The invention relates to a method for operating a gear pump according to the preamble of
Es ist bekannt, Öl, insbesondere Motoröl, eines Ölkreislaufs eines Fahrzeugs mittels einer Zahnradpumpe zu fördern. Die Zahnradpumpe kann dabei beispielsweise als Innenradzahnradpumpe ausgebildet sein, bei der wenigstens ein außenverzahntes Zahnrad in Zahneingriff mit wenigstens einem innenverzahnten Zahnrad ist. Eine derartige Innenzahnradpumpe wird üblicherweise über das innenverzahnte Zahnrad angetrieben. Weiter ist es auch bekannt, eine Zahnradpumpe als Außenzahnradpumpe auszuführen, bei der wenigstens ein außenverzahntes Zahnrad in Zahneingriff mit wenigstens einem weiteren außenverzahnten Zahnrad ist. Die Außenzahnradpumpe wird dabei mittels wenigstens eines dieser außenverzahnten Zahnräder angetrieben. Die Förderung des Öls bzw. der zu fördernden Flüssigkeit erfolgt dabei mittels der Zahnlücken zwischen den einzelnen Zähnen der Zahnräder. Diese Zahnlücken bilden Förderkammern aus, mittels denen die zu fördernde Flüssigkeit in Drehrichtung des jeweiligen Zahnrads gefördert wird.It is known to promote oil, in particular engine oil, an oil circuit of a vehicle by means of a gear pump. The gear pump may be formed, for example, as an internal gear pump, wherein at least one externally toothed gear meshing with at least one internally toothed gear. Such an internal gear pump is usually driven by the internal gear. Furthermore, it is also known to design a gear pump as an external gear pump in which at least one externally toothed gear meshes with at least one further externally toothed gear. The external gear pump is driven by means of at least one of these externally toothed gears. The promotion of the oil or the liquid to be delivered takes place by means of the tooth spaces between the individual teeth of the gears. These tooth gaps form delivery chambers, by means of which the liquid to be conveyed is conveyed in the direction of rotation of the respective toothed wheel.
Des Weiteren ist es auch bekannt, bei einer Außenzahnradpumpe die Zahnräder axial zu teilen bzw. wenigstens zwei Zahnräder, in Axialrichtung gesehen, hintereinander anzuordnen. Die geteilten Zahnräder werden dann üblicherweise um eine halbe Zahnteilung relativ zueinander verdreht angeordnet. Auf diese Weise können die Amplituden von beim Betrieb der Zahnradpumpe auftretenden Druckpulsationen verringert werden, da das Volumen der Förderkammern verkleinert und die Viskosität der Flüssigkeit beim Strömen der Flüssigkeit von einer Förderkammer zur benachbarten Förderkammer dämpfend wirkt. Zu hohe Amplituden der Druckpulsationen können beispielsweise in einem Ölkreislauf häufig zu einer Überbelastung von Ölkühlern, Überdruckventilen und weiteren Bauteilen des Ölkreislaufs führen.Furthermore, it is also known to axially divide the gears in an external gear pump or at least two gears, seen in the axial direction, to be arranged one behind the other. The split gears are then usually arranged rotated by half a tooth pitch relative to each other. In this way, the amplitudes of occurring during operation of the gear pump pressure pulsations can be reduced because the volume of the delivery chambers decreases and the viscosity of the liquid during the flow of liquid from one delivery chamber to the adjacent Delivery chamber dampening effect. Too high amplitudes of the pressure pulsations, for example, in an oil circuit often lead to an overload of oil coolers, pressure relief valves and other components of the oil circuit.
Aus der
Die Verdrehung der geteilten Zahnräder relativ zueinander wirkt sich jedoch negativ auf die Saugfähigkeit der Zahnradpumpe und somit auch auf die Förderleistung der Zahnradpumpe aus, insbesondere aufgrund des Strömens der zu fördernden Flüssigkeit von einer Förderkammer zur benachbarten Förderkammer. Dies ist beispielsweise bei der Verwendung einer Zahnradpumpe in einem Ölkreislauf eines Fahrzeugs in definierten Betriebssituationen der Zahnradpumpe problematisch.The rotation of the split gears relative to each other, however, has a negative effect on the absorbency of the gear pump and thus also on the delivery rate of the gear pump, in particular due to the flow of liquid to be conveyed from one delivery chamber to the adjacent delivery chamber. This is problematic, for example, when using a gear pump in an oil circuit of a vehicle in defined operating situations of the gear pump.
Es ist daher Aufgabe der Erfindung, ein Verfahren zum Betreiben einer Zahnradpumpe und eine Zahnradpumpe bereitzustellen, bei denen der Betrieb der Zahnradpumpe auf einfache und effektive Weise optimiert ist.It is therefore an object of the invention to provide a method for operating a gear pump and a gear pump, in which the operation of the gear pump is optimized in a simple and effective manner.
Diese Aufgabe wird durch die Merkmale der unabhängigen Patentansprüche gelöst. Bevorzugte Weiterbildungen sind in den Unteransprüchen offenbart.This object is solved by the features of the independent claims. Preferred developments are disclosed in the subclaims.
Gemäß Patentanspruch 1 wird ein Verfahren zum Betreiben einer Zahnradpumpe, insbesondere zur Förderung von Öl in einem Ölkreislauf eines Fahrzeugs, vorgeschlagen, wobei eine Fördereinrichtung mit wenigstens zwei in einem Gehäuse angeordneten, insbesondere außenverzahnten oder als Stirnräder ausgebildeten, Zahnrädern vorgesehen ist, wobei mittels der Zahnräder eine zu fördernde Flüssigkeit ausgehend von wenigstens einem Gehäuseeinlass hin zu wenigstens einem Gehäuseauslass gefördert werden kann, und wobei die Zahnräder, in Axialrichtung gesehen, hintereinander angeordnet sind. Erfindungsgemäß ist eine Stelleinrichtung vorgesehen, mittels der die Zahnräder in Abhängigkeit von den Druckverhältnissen im Inneren des Gehäuses, insbesondere in Abhängigkeit vom Saugunterdruck am Gehäuseeinlass und/oder in Abhängigkeit vom Flüssigkeitsgegendruck am Gehäuseauslass, relativ zueinander verdreht und/oder relativ zueinander verlagert werden.According to
Auf diese Weise wird der Betrieb der Zahnradpumpe auf einfache und effektive Weise optimiert, da die Zahnräder nun in Abhängigkeit von den Druckverhältnissen im Inneren des Gehäuses relativ zueinander verdreht und/oder relativ zueinander verlagert werden. Über die Druckverhältnisse im Inneren des Gehäuses kann zuverlässig erfasst werden, ob aktuell eine besonders hohe Saugkraft der Zahnradpumpe und somit eine besonders hohe Förderleistung der Zahnradpumpe erforderlich ist oder nicht. Die Zahnräder können dann beispielsweise derart relativ zueinander verdreht und/oder relativ zueinander verlagert werden, dass die Förderleistung der Zahnradpumpe besonders hoch ist oder die Amplituden der Druckpulsationen der Zahnradpumpe möglichst gering sind. Zudem können die Zahnräder auch in Zwischenstellungen verlagert werden, die eine ausreichende Förderleistung und gleichzeitig verringerte Amplituden der Druckpulsationen sicherstellen.In this way, the operation of the gear pump is optimized in a simple and effective manner, since the gears are now rotated in dependence on the pressure conditions in the interior of the housing relative to each other and / or displaced relative to each other. About the pressure conditions inside the housing can be reliably detected, whether currently a particularly high suction force of the gear pump and thus a particularly high flow rate of the gear pump is required or not. The gears can then for example be rotated relative to each other and / or relocated relative to each other, that the capacity of the gear pump is particularly high or the amplitudes of the pressure pulsations of the gear pump are as low as possible. In addition, the gears can also be displaced in intermediate positions, which ensure a sufficient flow rate and simultaneously reduced amplitudes of the pressure pulsations.
Die Zahnräder können dabei, in Axialrichtung gesehen, mit einem definierten Spaltabstand voneinander beabstandet in dem Gehäuse angeordnet sein. Bevorzugt ist es jedoch, wenn die hintereinander angeordneten Zahnräder miteinander in Anlage sind, um eine besonders kompakte Bauweise zu realisieren.The gears can, viewed in the axial direction, be spaced from each other with a defined gap spacing in the housing. However, it is preferred if the successively arranged toothed wheels are in contact with one another in order to realize a particularly compact construction.
Bevorzugt sind die Zahnräder derart in dem Gehäuse angeordnet, dass ihre Drehachsen im Wesentlichen kongruent oder parallel zueinander ausgerichtet sind, um die Zahnradpumpe besonders einfach und effektiv auszubilden. Weiter bevorzugt werden die Zahnräder mittels der Stelleinrichtung in Abhängigkeit von den Druckverhältnissen im Inneren des Gehäuses relativ zueinander axial verdreht und/oder relativ zueinander in Radialrichtung verlagert. So können die Saugfähigkeit und die Amplituden der Druckpulsationen der Zahnradpumpe einfach und effektiv verstellt bzw. eingestellt werden.Preferably, the gears are arranged in the housing such that their axes of rotation are substantially congruent or aligned parallel to each other to form the gear pump particularly simple and effective. More preferably, the gears are axially rotated by means of the adjusting device in dependence on the pressure conditions in the interior of the housing relative to each other and / or displaced relative to each other in the radial direction. Thus, the absorbency and the amplitudes of the pressure pulsations of the gear pump can be easily and effectively adjusted or adjusted.
In einer bevorzugten Verfahrensführung weisen die Zahnräder eine im Wesentlichen identische radiale Außenkontur auf. Die Zahnräder sind dann in einer Grundstellung, in Axialrichtung gesehen, zueinander fluchtend angeordnet. Sofern der Flüssigkeitsgegendruck am Gehäuseauslass dabei wenigstens einen definierten Minimalwert unterschreitet, werden die Zahnräder von einer nicht der Grundstellung entsprechenden Stellung mittels der Stelleinrichtung in die Grundstellung verlagert. In dieser Grundstellung ist die Saugfähigkeit bzw. die Saugkraft der Zahnradpumpe am größten. Durch die Verlagerung der Zahnräder in die Grundstellung wird somit zuverlässig sichergestellt, dass die Förderleistung der Zahnradpumpe maximal ist. In einem Ölkreislauf eines Fahrzeugs ist diese Grundstellung der Zahnräder beispielsweise bei einem Start einer Brennkraftmaschine des Fahrzeugs vorteilhaft, da so der Öldruck besonders rasch aufgebaut wird und Luftblasen schnell abgebaut werden. Bei einem derartigen Start der Brennkraftmaschine ist der Flüssigkeitsgegendruck am Gehäuseauslass besonders gering. Ebenso ist die Grundstellung in einem Ölkreislauf eines Fahrzeugs bei niedrigen Drehzahlen der Zahnradpumpe und hohen Öltemperaturen vorteilhaft, da trotz des eine geringe Viskosität aufweisenden Öls sogenannte Spaltverluste durch das Strömen des Öls zwischen den Förderkammern und in den Lagerstellen der Pumpe und der Brennkraftmaschine besser kompensiert wird. In dieser Betriebssituation ist der Flüssigkeitsgegendruck am Gehäuseauslass ebenfalls besonders gering.In a preferred method, the gears have a substantially identical radial outer contour. The gears are then arranged in a basic position, seen in the axial direction, aligned with each other. If the liquid back pressure at the housing outlet falls below at least a defined minimum value, the gears are shifted from a position not corresponding to the basic position by means of the adjusting device into the basic position. In this basic position, the suction capacity or the suction force of the gear pump is greatest. By the displacement of the gears in the basic position is thus reliably ensured that the capacity of the gear pump is maximum. In an oil circuit of a vehicle, this basic position of the gears, for example, at a start of an internal combustion engine of the vehicle advantageous because the oil pressure is built up so quickly and air bubbles are degraded quickly. In such a start of the internal combustion engine, the liquid back pressure at the housing outlet is particularly low. Likewise, the basic position in an oil circuit of a vehicle at low speeds of the gear pump and high oil temperatures is advantageous, since despite the low viscosity oil so-called gap losses is better compensated by the flow of oil between the delivery chambers and in the bearing points of the pump and the internal combustion engine. In this operating situation, the liquid back pressure at the housing outlet is also very low.
Weiter bevorzugt werden, sofern der Flüssigkeitsgegendruck am Gehäuseauslass den wenigstens einen Minimalwert nicht unterschreitet, die in der Grundstellung angeordneten Zahnräder mittels der Stelleinrichtung relativ zueinander verdreht und/oder relativ zueinander verlagert. Auf diese Weise werden die Amplituden der Druckpulsationen verringert, wenn die maximale Saugfähigkeit bzw. Saugkraft der Zahnradpumpe nicht benötigt wird.Further, if the liquid back pressure at the housing outlet does not fall below the at least one minimum value, the gears arranged in the basic position are rotated relative to one another by means of the adjusting device and / or displaced relative to one another. In this way, the amplitudes of the pressure pulsations are reduced when the maximum suction or suction force of the gear pump is not needed.
Bevorzugt werden die Zahnräder, sofern der Flüssigkeitsgegendruck am Gehäuseauslass wenigstens einen definierten, größer als der Minimalwert ausgebildeten Maximalwert überschreitet, in eine Maximalstellung verlagert, in der die Zahnräder um eine halbe Zahnteilung relativ zueinander verdreht angeordnet sind. In dieser Maximalstellung sind die Amplituden der Druckpulsationen besonders gering. Der Flüssigkeitsgegendruck am Gehäuseauslass ist in einem Ölkreislauf eines Fahrzeugs üblicherweise bei höheren Drehzahlen der Zahnradpumpe besonders groß.If the fluid back pressure at the housing outlet exceeds at least one defined maximum value formed greater than the minimum value, the toothed wheels are preferably displaced into a maximum position in which the toothed wheels are arranged rotated by half a tooth pitch relative to one another. In this maximum position, the amplitudes of the pressure pulsations are particularly low. The fluid back pressure at the housing outlet is usually particularly high in an oil circuit of a vehicle at higher speeds of the gear pump.
Zur Lösung der bereits genannten Aufgabe wird ferner eine Zahnradpumpe, insbesondere zur Förderung von Öl in einem Ölkreislauf eines Fahrzeugs, vorgeschlagen, mit einer Fördereinrichtung, die wenigstens zwei in einem Gehäuse angeordnete, insbesondere außenverzahnte und/oder als Stirnräder ausgebildete, Zahnräder aufweist, wobei mittels der Zahnräder eine zu fördernde Flüssigkeit ausgehend von wenigstens einem Gehäuseeinlass hin zu wenigstens einem Gehäuseauslass gefördert werden kann, und wobei die Zahnräder, in Axialrichtung gesehen, insbesondere mit einem definiertem Spaltabstand, hintereinander angeordnet sind. Erfindungsgemäß ist eine Stelleinrichtung vorgesehen, mittels der die Zahnräder in Abhängigkeit von den Druckverhältnissen im Inneren des Gehäuses, insbesondere in Abhängigkeit vom Saugunterdruck am Gehäuseeinlass und/oder in Abhängigkeit vom Flüssigkeitsgegendruck am Gehäuseauslass, relativ zueinander verdreht und/oder relativ zueinander verlagert werden können.To solve the object mentioned above, a gear pump, in particular for the promotion of oil in an oil circuit of a vehicle, proposed with a conveyor having at least two arranged in a housing, in particular externally toothed and / or formed as spur gears, gears, by means of A fluid to be conveyed can be conveyed from the toothed wheels starting from at least one housing inlet to at least one housing outlet, and wherein the toothed wheels, viewed in the axial direction, are arranged one behind the other, in particular with a defined gap distance. According to the invention, an adjusting device is provided by means of which the gears can be rotated relative to one another and / or displaced relative to one another in dependence on the pressure conditions in the interior of the housing, in particular as a function of the suction vacuum at the housing inlet and / or as a function of the liquid back pressure at the housing outlet.
Die sich durch die erfindungsgemäße Zahnradpumpe ergebenden Vorteile sind identisch mit den bereits gewürdigten Vorteilen des erfindungsgemäßen Verfahrens, so dass diese an dieser Stelle nicht wiederholt werden.The advantages resulting from the gear pump according to the invention are identical to the already appreciated advantages of the method according to the invention, so that they are not repeated at this point.
In einer bevorzugten Ausführung der Zahnradpumpe ist eine Fixiereinrichtung vorgesehen, mittels der wenigstens ein, ein Stell-Zahnrad ausbildendes Zahnrad relativ zu wenigstens einem anderen Zahnrad verlagerbar und/oder verdrehbar an dem Gehäuse festgelegt ist. Auf diese Weise können die Zahnräder besonders einfach relativ zueinander verdreht und/oder relativ zueinander verlagert werden.In a preferred embodiment of the gear pump, a fixing device is provided, by means of which at least one, a setting gear forming gear relative to at least one other gear is displaceable and / or rotatably fixed to the housing. In this way, the gears can be particularly easily rotated relative to each other and / or displaced relative to each other.
Vorzugsweise weist die Stelleinrichtung wenigstens ein Vorspannelement auf, mittels dem das Stell-Zahnrad in eine Grundstellung vorgespannt werden kann. Auf diese Weise kann das Stell-Zahnrad einfach und zuverlässig in die Grundstellung verlagert werden, da es mittels des Vorspannelements in diese Grundstellung gedrückt bzw. vorgespannt wird. Bevorzugt ist das Vorspannelement dabei durch ein Federelement, insbesondere durch eine Drehfeder, gebildet, um das Vorspannelement funktionssicher und einfach auszubilden.Preferably, the adjusting device has at least one biasing element, by means of which the adjusting gear can be biased into a basic position. In this way, the adjusting gear can be easily and reliably moved to the normal position, since it is pressed or biased by means of the biasing member in this basic position. Preferably, the biasing element is formed by a spring element, in particular by a torsion spring, in order to make the biasing element functionally reliable and simple.
Weiter bevorzugt wirkt das Vorspannelement mit einem Anschlag, insbesondere mit wenigstens einem Anschlagelement, zusammen, der eine Verdrehung und/oder Verlagerung des in der Grundstellung angeordneten Stell-Zahnrads in wenigstens eine definierte Richtung verhindert. So kann eine ungewünschte Verdrehung und/oder Verlagerung des Stell-Zahnrads in wenigstens eine definierte Richtung zuverlässig verhindert werden.More preferably, the biasing member cooperates with a stop, in particular with at least one stop element, which prevents rotation and / or displacement of the arranged in the basic position adjusting gear in at least one defined direction. So can an unwanted twisting and / or displacement of the adjusting gear in at least one defined direction can be reliably prevented.
Weiter bevorzugt verlagert und/oder verdreht sich das in der Grundstellung angeordnete Stell-Zahnrad bei definierten Druckverhältnissen im Gehäuse ausgehend von der Grundstellung relativ zu dem wenigstens einen anderen Zahnrad. Durch diese Verlagerung und/oder Verdrehung des Stell-Zahnrads wird das Vorspannelement dann unter Aufbau einer Rückstellkraft gespannt. Auf diese Weise kann die Verdrehung und/oder Verlagerung der Zahnräder relativ zueinander in Abhängigkeit von den Druckverhältnissen im Inneren des Gehäuses besonders einfach und zuverlässig realisiert werden. Insbesondere ist es nicht erforderlich, die Verdrehung und/oder Verlagerung der Zahnräder aufwendig und störanfällig mittels einer Regel- und/oder Steuereinrichtung zu regeln bzw. zu steuern. Die Zahnradpumpe ist daher auch besonders kostengünstig ausgebildet.More preferably displaced and / or rotated in the basic position arranged adjusting gear at defined pressure conditions in the housing, starting from the basic position relative to the at least one other gear. By this displacement and / or rotation of the adjusting gear, the biasing member is then stretched under construction of a restoring force. In this way, the rotation and / or displacement of the gears relative to one another depending on the pressure conditions in the interior of the housing can be realized particularly easily and reliably. In particular, it is not necessary to regulate or control the rotation and / or displacement of the gears in a complex and troublesome manner by means of a regulating and / or control device. The gear pump is therefore also formed particularly inexpensive.
Vorzugsweise ist ein Anschlagelement vorgesehen, mittels dem die Verlagerung und/oder Verdrehung des in der Grundstellung angeordneten Stell-Zahnrads auf ein definiertes Maß begrenzt werden kann. Auf diese Weise wird zuverlässig und einfach sichergestellt, dass sich das Stell-Zahnrad nur in einem definierten Maß relativ zu dem wenigstens einen anderen Zahnrad verlagern kann.Preferably, a stop element is provided by means of which the displacement and / or rotation of the arranged in the basic position adjusting gear can be limited to a defined extent. In this way it is reliably and easily ensured that the adjusting gear can move only in a defined degree relative to the at least one other gear.
Konkret kann die Zahnradpumpe beispielsweise als Innenzahnradpumpe ausgebildet sein, wobei die wenigstens zwei Zahnräder durch außenverzahnte Zahnräder gebildet sind, die in Zahneingriff mit wenigstens einem innenverzahnten Zahnradelement sind. Bevorzugt bildet dabei das innenverzahnte Zahnradelement oder ein außenverzahntes Zahnradelement, das kein Stell-Zahnrad ausbildet, ein Antriebszahnrad zum Antreiben der Innenzahnradpumpe aus, um die Zahnradpumpe besonders einfach antreiben zu können.Specifically, the gear pump may be formed, for example, as an internal gear pump, wherein the at least two gears are formed by externally toothed gears, which are in meshing engagement with at least one internally toothed gear member. Preferably, the internally toothed gear element or an externally toothed gear element, which does not form an adjusting gear, forms a drive gear for driving the internal gear pump in order to be able to drive the gear pump particularly easily.
Bevorzugt weist die Fixiereinrichtung ein Fixierelement auf, mittels dem das Stell-Zahnrad relativ zu dem Gehäuse verlagerbar an dem Gehäuse festgelegt ist, wobei das Stell-Zahnrad unter Ausbildung einer ersten Drehachse drehbar an dem Fixierelement festgelegt ist, wobei das Fixierelement unter Ausbildung einer im Wesentlichen parallel zur ersten Drehachse angeordneten, zweiten Drehachse drehbar an dem Gehäuse festgelegt ist, und wobei das Stell-Zahnrad durch Verdrehen des Fixierelements relativ zu dem Gehäuse verlagert werden kann. Auf diese Weise kann das Stell-Zahnrad besonders einfach und funktionssicher relativ zu dem wenigstens einem anderen Zahnrad verlagert und/oder verdreht werden. Bevorzugt ist dabei vorgesehen, dass das Fixierelement im Wesentlichen Z-förmig ausgebildet ist, um das Fixierelement funktionsoptimiert auszubilden.Preferably, the fixing device has a fixing element, by means of which the adjusting gear is fixed relative to the housing displaceable on the housing, wherein the adjusting gear is rotatably fixed to form a first axis of rotation on the fixing element, wherein the fixing element to form a substantially arranged parallel to the first axis of rotation, the second axis of rotation is rotatably attached to the housing, and wherein the adjusting gear can be displaced by rotation of the fixing element relative to the housing. This way you can the adjusting gear particularly simple and reliable relative to the at least one other gear shifted and / or rotated. Preferably, it is provided that the fixing element is formed substantially Z-shaped to form the fixing function optimized.
Weiter bevorzugt wird das Vorspannelement durch Drehen des Fixierelements in eine erste Drehrichtung gespannt. Das Vorspannelement wird dann durch Drehen des Fixierelements in eine zu der ersten Drehrichtung entgegengesetzte, zweite Drehrichtung entspannt. Auf diese Weise kann das Stell-Zahnrad besonders einfach mittels des Vorspannelements in die Grundstellung vorgespannt werden. Bevorzugt ist dabei vorgesehen, dass das Vorspannelement mit einem Endbereich an einem aus dem Gehäuse ragenden Bereich des Fixierelements festgelegt ist, um das Vorspannelement auf besonders einfache Weise an dem Fixierelement befestigen zu können.More preferably, the biasing element is tensioned by rotating the fixing in a first direction of rotation. The biasing element is then relaxed by rotating the fixing in a direction opposite to the first direction of rotation, the second direction of rotation. In this way, the adjusting gear can be particularly easily biased by the biasing member in the basic position. Preferably, it is provided that the biasing element is fixed with an end portion on a protruding from the housing portion of the fixing element in order to fasten the biasing member in a particularly simple manner to the fixing element can.
Alternativ zur Ausbildung als Innenzahnradpumpe kann die Zahnradpumpe auch als Außenzahnradpumpe ausgebildet sein, wobei die wenigstens zwei Zahnräder durch außenverzahnte Zahnräder gebildet sind und Antriebszahnräder zum Antreiben der Außenzahnradpumpe ausbilden, und wobei jedes dieser Antriebszahnräder jeweils in Zahneingriff mit einem korrespondierenden außenverzahnten Zahnrad ist.Alternatively to the embodiment as an internal gear pump, the gear pump may also be formed as an external gear pump, wherein the at least two gears are formed by externally toothed gears and drive gears to drive the external gear pump, and wherein each of these drive gears is in meshing engagement with a corresponding externally toothed gear.
Bevorzugt weist die Fixiereinrichtung dabei eine drehbar an dem Gehäuse festgelegte Antriebswelle zum Antreiben der Antriebszahnräder auf, wobei wenigstens ein Antriebszahnrad drehfest mit der Antriebswelle verbunden ist, wobei wenigstens ein, das Stell-Zahnrad ausbildende Antriebszahnrad relativ zur Antriebswelle axial verdrehbar an der Antriebswelle festgelegt ist, und wobei die Antriebswelle mittels des Vorspannelements drehmomentübertragend mit dem Stell-Zahnrad verbunden ist. So kann das Stell-Zahnrad besonders einfach relativ zu dem anderen Zahnrad verdrehbar festgelegt werden.Preferably, the fixing device has a rotatably fixed to the housing drive shaft for driving the drive gears, wherein at least one drive gear rotatably connected to the drive shaft, wherein at least one, the adjusting gear forming drive gear is fixed relative to the drive shaft axially rotatable on the drive shaft, and wherein the drive shaft is connected by means of the biasing element to transmit torque to the adjusting gear. Thus, the adjusting gear can be particularly easily set rotatable relative to the other gear.
Bevorzugt wird das Vorspannelement durch Drehen des Stell-Zahnrads relativ zur Antriebswelle in eine erste Drehrichtung gespannt. Das Vorspannelement wird dann durch Drehen des Stell-Zahnrads relativ zur Antriebswelle in eine zu der ersten Drehrichtung entgegengesetzte, zweite Drehrichtung entspannt. So kann das Stell-Zahnrad ebenfalls besonders einfach mittels des Vorspannelements in die Grundstellung vorgespannt werden. Bevorzugt ist dabei vorgesehen, dass das Vorspannelement, in Axialrichtung gesehen, zwischen den Antriebszahnrädern angeordnet ist, um eine besonders kompakte Bauweise zu realisieren. Alternativ und/oder zusätzlich kann das Vorspannelement aber auch zwischen dem Stell-Zahnrad und einer Gehäusewand angeordnet sein oder aus dem Gehäuse herausragen.Preferably, the biasing member is biased by rotating the adjusting gear relative to the drive shaft in a first direction of rotation. The biasing member is then relaxed by turning the adjusting gear relative to the drive shaft in a direction opposite to the first rotational direction, second rotational direction. Thus, the adjusting gear can also be biased particularly easy by means of the biasing member in the basic position. It is preferably provided that the biasing element, in Seen axially, between the drive gears is arranged to realize a particularly compact design. Alternatively and / or additionally, however, the biasing element can also be arranged between the adjusting gear and a housing wall or protrude out of the housing.
Ferner wird auch ein Fahrzeug, insbesondere ein Nutzfahrzeug, und/oder eine Brennkraftmaschine zur Durchführung des erfindungsgemäßen Verfahrens und/oder mit der erfindungsgemäßen Zahnradpumpe beansprucht. Die sich hieraus ergebenden Vorteile sind identisch mit den bereits gewürdigten Vorteilen des erfindungsgemäßen Verfahrens und/oder der erfindungsgemäßen Zahnradpumpe, so dass diese an dieser Stelle nicht wiederholt werden. Die Brennkraftmaschine kann dabei beispielsweise auch als stationäre Brennkraftmaschine oder als Marine-Brennkraftmaschine ausgebildet sein.Furthermore, a vehicle, in particular a commercial vehicle, and / or an internal combustion engine for carrying out the method according to the invention and / or claimed with the gear pump according to the invention. The resulting advantages are identical to the already acknowledged advantages of the method according to the invention and / or the gear pump according to the invention, so that they are not repeated at this point. The internal combustion engine can be designed, for example, as a stationary internal combustion engine or as a marine internal combustion engine.
Die vorstehend erläuterten und/oder in den Unteransprüchen wiedergegebenen vorteilhaften Aus- und/oder Weiterbildungen der Erfindung können - außer zum Beispiel in den Fällen eindeutiger Abhängigkeiten oder unvereinbarer Alternativen - einzeln oder aber auch in beliebiger Kombination miteinander zur Anwendung kommen.The advantageous embodiments and / or further developments of the invention explained above and / or reproduced in the dependent claims can be used individually or else in any desired combination with one another, for example in the case of clear dependencies or incompatible alternatives.
Die Erfindung und ihre vorteilhaften Aus- und/oder Weiterbildungen sowie deren Vorteile werden nachfolgend anhand von Zeichnungen lediglich beispielhaft näher erläutert.The invention and its advantageous embodiments and / or developments and their advantages will be explained in more detail by way of example only with reference to drawings.
Es zeigen:
- Fig. 1
- in einer Ansicht von oben eine erfindungsgemäße Innenzahnradpumpe mit geöffnetem Gehäuse in einer ersten Betriebssituation;
- Fig. 2
- in einer Darstellung gemäß
Fig. 1 die Innenzahnradpumpe in einer zweiten Betriebssituation; - Fig. 3
- in einer schematischen Schnittdarstellung eine Stelleinrichtung der Innenzahnradpumpe;
- Fig. 4
- eine schematische Darstellung, anhand der die Funktionsweise der Stelleinrichtung erläutert wird;
- Fig. 5
- in einer Darstellung von oben eine erfindungsgemäße Außenzahnradpumpe mit geöffnetem Gehäuse in einer ersten Betriebssituation;
- Fig. 6
- in einer Darstellung gemäß
Fig. 5 die Außenzahnradpumpe in einer zweiten Betriebssituation; und - Fig. 7
- in einer schematischen Schnittdarstellung eine Stelleinrichtung der Außenzahnradpumpe.
- Fig. 1
- in a view from above an inventive internal gear pump according to the invention with the housing open in a first operating situation;
- Fig. 2
- in a representation according to
Fig. 1 the internal gear pump in a second operating situation; - Fig. 3
- in a schematic sectional view of an adjusting device of the internal gear pump;
- Fig. 4
- a schematic representation, based on the operation of the adjusting device is explained;
- Fig. 5
- in a representation from above an external gear pump according to the invention with the housing open in a first operating situation;
- Fig. 6
- in a representation according to
Fig. 5 the external gear pump in a second operating situation; and - Fig. 7
- in a schematic sectional view of an adjusting device of the external gear pump.
In
Wie in
Gemäß
Wie aus
Gemäß
Des Weiteren wird das Stellelement 25 hier beispielhaft mittels der Drehfeder 31 gegen ein in
Wie aus
In den
Wie in
- 11
- InnenzahnradpumpeInternal gear pump
- 33
- Gehäusecasing
- 55
- Gehäuseeinlasshousing inlet
- 77
- Gehäuseauslasshousing outlet
- 99
- innenverzahntes Stirnradinternally toothed spur gear
- 1111
- außenverzahntes Stirnradexternally toothed spur gear
- 1313
- außenverzahntes Stirnradexternally toothed spur gear
- 1515
- Zahnlückegap
- 1919
- Achseaxis
- 2121
- Stelleinrichtungsetting device
- 2323
- Fixiereinrichtungfixing
- 2525
- Fixierelementfixing
- 2727
- Achseaxis
- 2929
- Achseaxis
- 3131
- Drehfedertorsion spring
- 3333
- erster Endbereichfirst end area
- 3535
- Endbereichend
- 3737
- zweiter Endbereichsecond end area
- 3939
- Festlegungsstelledetermination Agent
- 4141
- Anschlagelementstop element
- 4343
- Anschlagelementstop element
- 4545
- AußenzahnradpumpeExternal gear pump
- 4747
- Stirnradspur gear
- 4949
- Stirnradspur gear
- 5151
- Stirnradspur gear
- 5252
- Achseaxis
- 5353
- Antriebswelledrive shaft
- 5555
- Drehfedertorsion spring
- A1 A 1
- erste Drehachsefirst axis of rotation
- A2 A 2
- zweite Drehachsesecond axis of rotation
- R1 R 1
- erste Drehrichtungfirst direction of rotation
- R2 R 2
- zweite Drehrichtungsecond direction of rotation
Claims (18)
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102015001235.5A DE102015001235A1 (en) | 2015-02-03 | 2015-02-03 | Method for operating a gear pump and gear pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3054161A1 true EP3054161A1 (en) | 2016-08-10 |
EP3054161B1 EP3054161B1 (en) | 2020-07-15 |
Family
ID=54185823
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15002727.4A Active EP3054161B1 (en) | 2015-02-03 | 2015-09-22 | Method for operating a gear wheel pump and gear wheel pump |
Country Status (6)
Country | Link |
---|---|
US (1) | US10436082B2 (en) |
EP (1) | EP3054161B1 (en) |
CN (1) | CN105840499B (en) |
BR (1) | BR102015030185B1 (en) |
DE (1) | DE102015001235A1 (en) |
RU (1) | RU2699859C2 (en) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9902251B2 (en) * | 2016-01-26 | 2018-02-27 | Deere & Company | Recess-mounted hydraulic pump cartridge and work vehicle drivetrain therewith |
US11242850B2 (en) * | 2019-08-07 | 2022-02-08 | GM Global Technology Operations LLC | Scavenge gear assembly for an oil pump of a vehicle |
GB2592623A (en) * | 2020-03-04 | 2021-09-08 | Delphi Tech Ip Ltd | A pump assembly |
RU199143U1 (en) * | 2020-04-22 | 2020-08-19 | Публичное акционерное общество «Авиационная корпорация «Рубин» | Gerotor pump |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1231563B (en) * | 1963-01-16 | 1966-12-29 | Danfoss As | Adjustable gear pump |
GB2313411A (en) * | 1996-05-25 | 1997-11-26 | Concentric Pumps Ltd | Hydrostatic drive with variable output pump |
DE19746768A1 (en) | 1997-10-23 | 2000-12-21 | Bosch Gmbh Robert | Toothed gear pump or motor has shaft with outer toothing consisting of two toothed parts with offset teeth |
GB2443089A (en) * | 2006-10-18 | 2008-04-23 | Concentric Vfp Ltd | Split rotor variable output gerotor pump |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB8707127D0 (en) * | 1987-03-25 | 1987-04-29 | Blything W C | Hydraulic transmission |
CH679062A5 (en) * | 1988-10-24 | 1991-12-13 | Siegfried Eisenmann | |
US5092751A (en) | 1990-10-26 | 1992-03-03 | Viktora Dean C | Split gear pump mechanism with gear offset |
DE10334954A1 (en) * | 2003-07-31 | 2005-02-24 | Voith Turbo Gmbh & Co. Kg | hydraulic pump |
RU2376498C2 (en) * | 2004-12-30 | 2009-12-20 | Владислав Анатольевич Власенков | Rotor-piston controlled hydraulic machine |
GB2430237A (en) | 2005-06-11 | 2007-03-21 | Concentric Pumps Ltd | Variable output internal gear pump |
GB0620646D0 (en) | 2006-10-18 | 2006-11-29 | Concentric Vfp Ltd | Pumps with filling slots |
ITBO20080686A1 (en) | 2008-11-13 | 2010-05-14 | Cnh Italia Spa | GEROTOR TYPE PUMP |
CN102536795A (en) * | 2011-12-27 | 2012-07-04 | 张意立 | Cone spring compensation gear pump |
DE102012009605A1 (en) * | 2012-05-15 | 2013-11-21 | Man Truck & Bus Ag | Method for compensating a change in the axle distance on the control drive of a valve-controlled internal combustion engine and control drive for a valve-controlled internal combustion engine |
-
2015
- 2015-02-03 DE DE102015001235.5A patent/DE102015001235A1/en not_active Withdrawn
- 2015-09-22 EP EP15002727.4A patent/EP3054161B1/en active Active
- 2015-10-27 RU RU2015146371A patent/RU2699859C2/en active
- 2015-12-01 BR BR102015030185-5A patent/BR102015030185B1/en active IP Right Grant
-
2016
- 2016-02-02 US US15/013,019 patent/US10436082B2/en active Active
- 2016-02-03 CN CN201610075341.4A patent/CN105840499B/en active Active
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE1231563B (en) * | 1963-01-16 | 1966-12-29 | Danfoss As | Adjustable gear pump |
GB2313411A (en) * | 1996-05-25 | 1997-11-26 | Concentric Pumps Ltd | Hydrostatic drive with variable output pump |
DE19746768A1 (en) | 1997-10-23 | 2000-12-21 | Bosch Gmbh Robert | Toothed gear pump or motor has shaft with outer toothing consisting of two toothed parts with offset teeth |
GB2443089A (en) * | 2006-10-18 | 2008-04-23 | Concentric Vfp Ltd | Split rotor variable output gerotor pump |
Also Published As
Publication number | Publication date |
---|---|
DE102015001235A1 (en) | 2016-08-04 |
EP3054161B1 (en) | 2020-07-15 |
RU2699859C2 (en) | 2019-09-11 |
BR102015030185A2 (en) | 2016-10-04 |
BR102015030185B1 (en) | 2022-11-16 |
RU2015146371A (en) | 2017-05-04 |
CN105840499A (en) | 2016-08-10 |
RU2015146371A3 (en) | 2019-03-07 |
CN105840499B (en) | 2020-06-26 |
US20160230620A1 (en) | 2016-08-11 |
US10436082B2 (en) | 2019-10-08 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
WO2010043193A1 (en) | Drive shaft assembly for a transmission of a motor vehicle | |
EP3054161A1 (en) | Method for operating a gear wheel pump and gear wheel pump | |
EP1574316A1 (en) | Drive for a twin-screw extruder | |
EP1927754A1 (en) | Inner geared pump | |
EP3184856B1 (en) | Planetary drive device and jet engine having a planetary drive device | |
DE102012001462A1 (en) | Internal gear pump comprises control bevel, which is provided in area of sealing segment side facing hollow wheel, and is extended out in peripheral direction of hollow wheel and broadens opening area of control groove | |
DE102014207202A1 (en) | Thermal management module | |
DE4303337C2 (en) | Gear machine | |
DE102006025367B4 (en) | Gear pump, in particular gear oil pump for vehicles | |
WO2017190903A1 (en) | Transmission comprising a pump mechanically driven on a ring gear of the transmission | |
DE102015204166A1 (en) | gearing | |
EP3686462A1 (en) | Toothed wheel for use in a gear transmission, gear pairing of a gear transmission and gear transmission with such a gear pairing | |
DE102015104316A1 (en) | Wave gear for an actuator of a steering system | |
DE102020126843A1 (en) | shaft-hub connection | |
DE102010004579A1 (en) | Valve train for operation of valves of four cylinders of combustion engine, has camshaft with carriers having rotary driving units at front ends, respectively, where driving units of adjacent carriers are engaged in axially movable manner | |
WO2010105877A1 (en) | Manual transmission | |
DE102012019906B3 (en) | Gear control oil pump, particularly external gear control oil pump for internal combustion engine of motor vehicle, comprises two conveyor gears and spring elements designed such that latter conveyor gear is pushed in intermediate position | |
DE102010020299A1 (en) | Pump e.g. rotary pump, has rotatable friction clutch link receiving rotational torque through friction gap in frictional engagement, where strength of frictional engagement and slippage are adjusted up to zero | |
WO2011124603A1 (en) | Power transmission | |
DE19646862C2 (en) | Coupling dressing | |
DE10247439B4 (en) | Transmission for windscreen wiper device and windscreen wiper device, which is provided with such a transmission | |
DE10139896A1 (en) | Differential with two cam parts | |
WO2008101904A1 (en) | Gerotor pump | |
DE102004058177A1 (en) | Gear wheel with two gear parts has two gear parts with bevel gearing which are braced against each other in axial direction by working spring force along axial gap | |
DE102020117895A1 (en) | Oil pump |
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 |
|
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 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: REQUEST FOR EXAMINATION WAS MADE |
|
17P | Request for examination filed |
Effective date: 20170207 |
|
RAP1 | Party data changed (applicant data changed or rights of an application transferred) |
Owner name: MAN TRUCK & BUS SE |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: GRANT OF PATENT IS INTENDED |
|
INTG | Intention to grant announced |
Effective date: 20200214 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: THE PATENT HAS BEEN GRANTED |
|
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: CH Ref legal event code: EP Ref country code: GB Ref legal event code: FG4D Free format text: NOT ENGLISH |
|
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: 502015012996 Country of ref document: DE |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 1291321 Country of ref document: AT Kind code of ref document: T Effective date: 20200815 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: FP |
|
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 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20201116 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: 20200715 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: 20200715 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: 20201016 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: 20201015 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: 20201015 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: 20200715 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: 20200715 |
|
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: 20200715 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: 20200715 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: 20200715 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: 20201115 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502015012996 Country of ref document: DE |
|
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: 20200715 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: 20200715 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: 20200715 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: 20200715 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: 20200715 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: 20200715 |
|
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: 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: 20200715 |
|
REG | Reference to a national code |
Ref country code: BE Ref legal event code: MM Effective date: 20200930 |
|
26N | No opposition filed |
Effective date: 20210416 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20201015 |
|
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: 20200922 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: 20200715 |
|
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: 20200715 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200930 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20201015 Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200922 Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200930 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200930 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 1291321 Country of ref document: AT Kind code of ref document: T Effective date: 20200922 |
|
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: 20200922 |
|
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: 20200715 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: 20200715 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: 20200715 |
|
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: 20200715 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: NL Payment date: 20230926 Year of fee payment: 9 Ref country code: IT Payment date: 20230920 Year of fee payment: 9 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: SE Payment date: 20230926 Year of fee payment: 9 Ref country code: FR Payment date: 20230926 Year of fee payment: 9 Ref country code: DE Payment date: 20230928 Year of fee payment: 9 |