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EP3054161B1 - Procede de fonctionnement d'une pompe à engrenages et pompe à engrenages - Google Patents

Procede de fonctionnement d'une pompe à engrenages et pompe à engrenages Download PDF

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Publication number
EP3054161B1
EP3054161B1 EP15002727.4A EP15002727A EP3054161B1 EP 3054161 B1 EP3054161 B1 EP 3054161B1 EP 15002727 A EP15002727 A EP 15002727A EP 3054161 B1 EP3054161 B1 EP 3054161B1
Authority
EP
European Patent Office
Prior art keywords
gearwheels
housing
gear pump
gearwheel
actuating
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.)
Active
Application number
EP15002727.4A
Other languages
German (de)
English (en)
Other versions
EP3054161A1 (fr
Inventor
Simon Bucher
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.)
MAN Truck and Bus SE
Original Assignee
MAN Truck and Bus SE
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Filing date
Publication date
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Publication of EP3054161A1 publication Critical patent/EP3054161A1/fr
Application granted granted Critical
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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 performing the method and / or with the gear pump according to claim 17.
  • the gear pump can be designed, for example, as an internal gear pump, in which at least one externally toothed gear meshes with at least one internally toothed gear.
  • Such an internal gear pump is usually driven via the internal gear.
  • a gear pump as an external gear pump, in which at least one externally toothed gear is in meshing engagement with at least one further externally toothed gear.
  • the external gear pump is driven by means of at least one of these external gear wheels.
  • the oil or the liquid to be pumped is conveyed by means of the tooth gaps between the individual teeth of the gear wheels. These tooth gaps form delivery chambers, by means of which the liquid to be delivered is conveyed in the direction of rotation of the respective gear wheel.
  • a gear machine with an engine results from at least two gear paths, the gear wheels of which are guided with their hubs on at least two shafts rotatably mounted in the housing.
  • the driven gearwheels of the at least two pairs of gearwheels are arranged together on one of the shafts and are non-rotatably coupled to this shaft via an external toothing formed on this shaft and an internal toothing formed in the hubs of the driven gearwheels.
  • the external toothing of the shaft here consists of at least two toothed parts which are spaced apart from one another and have a tooth offset, which are each assigned to one of the driven gearwheels. In this way, it is easily and reliably ensured that the gearwheels are fixed on the common shaft offset from one another by half a tooth pitch.
  • the publication GB 2 443 089 A which is considered to be the closest prior art, discloses a gear pump with two gearwheels arranged one behind the other, seen in the axial direction, inside a housing, the one gearwheel being displaceable relative to the first gearwheel by means of an eccentric arrangement.
  • Such a gear pump is also in the publications DE 1 231 563 A and GB 2 313 411 A disclosed.
  • a method for operating a gear pump, in particular for conveying oil in an oil circuit of a vehicle is proposed, a delivery device having at least two gear wheels arranged in a housing, in particular externally toothed or designed as spur gears, being provided, by means of the gear wheels a liquid to be pumped can be conveyed from at least one housing inlet to at least one housing outlet, and wherein the gearwheels, viewed in the axial direction, are arranged one behind the other.
  • an actuating device is provided by means of which the gearwheels are rotated relative to one another and / or displaced relative to one another depending on the pressure conditions in the interior of the housing, in particular depending on the suction vacuum at the housing inlet and / or depending on the liquid counterpressure at the housing outlet.
  • a fixing device by means of which at least one gear wheel, which forms an actuating gear wheel, is fixed on the housing such that it can be displaced and / or rotated relative to at least one other gear wheel.
  • the actuating device has at least one spring element as a prestressing element, by means of which the adjusting gear can be prestressed into a basic position.
  • the operation of the gear pump is optimized in a simple and effective manner, since the gear wheels are now rotated relative to one another and / or displaced relative to one another depending on the pressure conditions in the interior of the housing.
  • the pressure conditions inside the housing can be used to reliably determine whether a particularly high suction power of the gear pump and thus a particularly high delivery rate of the gear pump is currently required or not.
  • the gear wheels can then be rotated and / or displaced relative to one another in such a way, for example, that the delivery 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 shifted to intermediate positions, which ensure sufficient delivery and at the same time reduced amplitudes of the pressure pulsations.
  • the gearwheels When viewed in the axial direction, the gearwheels can be arranged at a defined gap distance from one another in the housing. However, it is preferred if the gears arranged one behind the other are in contact with one another in order to realize a particularly compact construction.
  • the gearwheels are preferably arranged in the housing such that their axes of rotation are aligned essentially congruently or parallel to one another, in order to make the gearwheel pump particularly simple and effective.
  • the gearwheels are further preferably rotated axially relative to one another and / or displaced relative to one another in the radial direction by means of the adjusting device as a function of the pressure conditions in the interior of the housing. In this way, the absorbency and the amplitudes of the pressure pulsations of the gear pump can be easily and effectively adjusted.
  • the gearwheels have an essentially identical radial outer contour.
  • the gearwheels are then arranged in alignment with one another in a basic position, seen in the axial direction. If the liquid back pressure at the housing outlet falls below at least a defined minimum value, the gearwheels are shifted from a position not corresponding to the basic position into the basic position by means of the adjusting device. In this basic position, the absorbency or suction power of the gear pump is greatest. By shifting the gearwheels into the basic position, it is reliably ensured that the delivery capacity of the gearwheel pump is at a maximum.
  • this basic position of the gearwheels is advantageous, for example, when starting an internal combustion engine of the vehicle, since the oil pressure is built up particularly quickly and air bubbles are quickly broken down.
  • the liquid counterpressure 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 are better compensated for by the oil flowing 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 particularly low.
  • the gearwheels arranged in the basic position are rotated relative to one another and / or displaced relative to one another by means of the adjusting device. In this way, the amplitudes of the pressure pulsations are reduced if the maximum absorbency or suction force of the gear pump is not required.
  • the gearwheels are preferably shifted to a maximum position in which the gearwheels are arranged rotated relative to one another by half a tooth pitch. In this maximum position, the amplitudes of the pressure pulsations are particularly low.
  • the liquid 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 conveying oil in an oil circuit of a vehicle, is also proposed, with a delivery device which has at least two gear wheels arranged in a housing, in particular externally toothed and / or designed as spur gears, whereby by means of a liquid to be conveyed can be conveyed from the gearwheels from at least one housing inlet to at least one housing outlet, and the gearwheels, viewed in the axial direction, in particular with a defined gap distance, are arranged one behind the other.
  • an actuating device is provided by means of which the gear wheels can be rotated relative to one another and / or displaced relative to one another depending on the pressure conditions in the interior of the housing, in particular depending on the suction vacuum at the housing inlet and / or depending on the liquid counterpressure at the housing outlet.
  • a fixing device by means of which at least one gear wheel, which forms an actuating gear wheel, is fixed on the housing such that it can be displaced and / or rotated relative to at least one other gear wheel.
  • the gearwheels can be rotated and / or displaced relative to one another in a particularly simple manner.
  • the adjusting device has at least one prestressing element, by means of which the adjusting gearwheel can be prestressed into a basic position.
  • the adjusting gear can be easily and reliably shifted into the basic position, since it is pressed or pretensioned into this basic position by means of the pretensioning element.
  • the biasing element is preferably formed by a spring element, in particular by a torsion spring, in order to make the biasing element functionally reliable and simple.
  • the prestressing element further preferably interacts with a stop, in particular with at least one stop element, which prevents rotation and / or displacement of the adjusting gear arranged in the basic position in at least one defined direction. This can result in unwanted twisting and / or displacement of the adjusting gear in at least one defined direction can be reliably prevented.
  • the adjusting gear arranged in the basic position rotates and / or rotates relative to the at least one other gear in the housing at defined pressure conditions in the housing, starting from the basic position.
  • the biasing element is then tensioned with the build-up of a restoring force.
  • the rotation and / or displacement of the gear wheels relative to one another can be implemented particularly simply and reliably as a function of the pressure conditions in the interior of the housing.
  • the gear pump is therefore particularly cost-effective.
  • a stop element is preferably provided, by means of which the displacement and / or rotation of the adjusting gear arranged in the basic position can be limited to a defined dimension. In this way, it is reliably and simply ensured that the actuating gear can only shift to a defined extent relative to the at least one other gear.
  • the gear pump can be designed, for example, as an internal gear pump, the at least two gear wheels being formed by externally toothed gear wheels which are in meshing engagement with at least one internally toothed gear element.
  • the internally toothed gear element or an externally toothed gear element, which does not form an actuating gear, preferably forms a drive gear for driving the internal gear pump in order to be able to drive the gear pump in a particularly simple manner.
  • the fixing device preferably has a fixing element, by means of which the adjusting gear is fixed to the housing such that it can be displaced relative to the housing, the adjusting gear being rotatably fixed to the fixing element while forming a first axis of rotation, the fixing element essentially forming a arranged parallel to the first axis of rotation, the second axis of rotation is rotatably fixed to the housing, and wherein the adjusting gear can be displaced relative to the housing by rotating the fixing element. That way the adjusting gear can be shifted and / or rotated in a particularly simple and reliable manner relative to the at least one other gear. It is preferably provided that the fixing element is essentially Z-shaped in order to make the fixing element functionally optimized.
  • the biasing element is further preferably tensioned by rotating the fixing element in a first direction of rotation.
  • the biasing element is then relaxed by rotating the fixing element in a second direction of rotation opposite to the first direction of rotation.
  • the adjusting gear can be pretensioned into the basic position in a particularly simple manner by means of the pretensioning element.
  • the prestressing element is fixed with an end region to a region of the fixing element protruding from the housing in order to be able to fasten the prestressing element to the fixing element in a particularly simple manner.
  • the gear pump can also be designed as an external gear pump, the at least two gear wheels being formed by externally toothed gear wheels and forming drive gear wheels for driving the external gear pump, and each of these drive gear wheels in meshing engagement with a corresponding externally toothed gear wheel.
  • the fixing device preferably has a drive shaft rotatably fixed to the housing for driving the drive gearwheels, at least one drive gearwheel being non-rotatably connected to the drive shaft, at least one drive gearwheel forming the actuating gearwheel being fixed axially rotatable on the drive shaft relative to the drive shaft. and wherein the drive shaft is connected to the actuating gear by means of the biasing element in a torque-transmitting manner.
  • the adjusting gear can be fixed in a particularly simple manner so that it can be rotated relative to the other gear.
  • the biasing element is preferably tensioned in a first direction of rotation by rotating the adjusting gearwheel relative to the drive shaft.
  • the biasing element is then relaxed by rotating the actuating gear relative to the drive shaft in a second direction of rotation opposite to the first direction of rotation.
  • the adjusting gear can also be biased into the basic position particularly easily by means of the biasing element.
  • the prestressing element in Seen in the axial direction, is arranged between the drive gears in order to realize a particularly compact design.
  • the prestressing element can also be arranged between the adjusting gearwheel and a housing wall or protrude from 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 with the gear pump according to the invention is also claimed.
  • the advantages resulting from this are identical to the advantages of the method according to the invention and / or the gear pump according to the invention that have already been recognized, so that they are not repeated here.
  • the internal combustion engine can for example also be designed as a stationary internal combustion engine or as a marine internal combustion engine.
  • a gear pump designed as an internal gear pump 1 is shown here by way of example.
  • 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 again via the housing outlet 7 3 exits.
  • the internal gear pump 1 has an internal gear arranged in the interior of the housing 3, 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 mesh with several, here exemplified with two externally toothed, also designed as spur gears 11, 13 gears.
  • the externally toothed spur gears 11, 13 are here, for example, identical or of identical construction and, in the axial direction x ( Fig. 3 ) seen, arranged one behind the other in the housing 3 with a defined gap distance.
  • the internally toothed spur gear 9 is driven in rotation by means of a suitable drive device, not shown in the figures.
  • the externally toothed spur gear 13 is axially rotatable, for example, on an axis 19.
  • the axis 19 is here, for example, rigid or immovable fixed to the housing 3.
  • the externally toothed spur gear 11 is exemplified here by means of an adjusting device 21 ( Fig. 3 ) can be displaced and rotated relative to the externally toothed spur gear 13 on the housing 3.
  • the externally toothed spur gear 11 can, for example, by means of the adjusting device 21 in a Fig. 2 shown basic position are arranged, in which the externally toothed spur gears 11, 13, seen in the axial direction x or in plan view, are arranged in alignment with each other.
  • the externally toothed spur gear 11 can also be arranged here, for example, in a maximum position in which the externally toothed spur gears 11, 13 are rotated relative to one another by half a tooth pitch.
  • 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, aligned parallel to one another.
  • the adjusting device 21 has a fixing device 23, by means of which the gear wheel 11, which forms an adjusting gear wheel, is fixed on the housing 3 such that it can be displaced or rotated relative to the housing 3 and thus also to the spur gear 13.
  • the fixing device 23 here comprises, for example, an essentially Z-shaped fixing element 25 which has an axis 27 which forms a first axis of rotation A 1 and on which the adjusting gear 11 is fixed in an axially rotatable manner.
  • the fixing element 25 also has an axis 29 which forms a second axis of rotation A 2 and by means of which the fixing element 25 is rotatably fixed to the housing 3.
  • the axes 27, 29 are offset from one another such that the second axis of rotation A 2 is arranged parallel to the first axis of rotation A 1 .
  • the actuating device 21 also has a biasing element, which is designed here, for example, as a torsion spring 31, by means of which the setting gearwheel 11 is moved into the basic position ( Fig. 2 ) is biased.
  • the torsion spring 31 is exemplified here by rotating the fixing element 25 in a first direction of rotation R 1 ( Fig. 4 ) around the second axis of rotation A 2 .
  • the torsion spring 31 is here, for example, with an end region 33 on a protruding from the housing 3 End region 35 of the fixing element 25 and fixed immovably or rigidly at a fixing point 39 on the vehicle side with a second end region 37.
  • the adjusting element 25 is here, for example, by means of the torsion spring 31 against an in Fig. 4 schematically shown stop element 41 biased.
  • the stop element 41 prevents rotation and / or displacement of the adjusting gear 11 arranged in the basic position in the first direction of rotation R 2 .
  • the torsion spring 31 is designed here, for example, in such a way that the fixing element 25 rotates in the housing 3 in the first direction of rotation R 1 at defined pressure conditions. As a result of this rotation, the torsion spring 31 is tensioned while building up a restoring force.
  • the adjusting 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 in such a way that the adjusting Gear 11 can only be moved to the maximum position.
  • the gear pump is designed here, for example, as an external gear pump 45.
  • the external gear pump 45 has a plurality of, here exemplarily two, external gear toothed gears designed here as spur gears 47, 49 for driving the external gear pump 45.
  • Each of these spur gears 47, 49 is here, for example, in meshing engagement with a corresponding gear, which is likewise designed here as a spur gear 51.
  • the spur gears 51 are axially rotatable, for example, on an axis 52.
  • the axis 52 is fixed, for example, rigidly or immovably on the housing 3.
  • the spur gears 47, 49, 51 are designed here to be identical or structurally identical.
  • the fixing device 23 here has a drive shaft 53 rotatably fixed to the housing 3 for driving the spur gears 47, 49.
  • the spur gear 47 is connected, for example, in a rotationally fixed manner to the drive shaft 53.
  • the spur gear 49 which forms an actuating gear, is fixed axially rotatably on the drive shaft 53 in relation to the drive shaft 53.
  • the two spur gears 47, 49 are connected here in a torque-transmitting manner by means of a biasing element designed as a torsion spring 55.
  • the torsion spring 55 is an example here, in the axial direction x seen, arranged between the spur gears 47, 49.
  • the torsion spring 55 is tensioned in a first direction of rotation by rotating the adjusting gear 49 relative to the drive shaft 53 and thus also relative to the gear 47. In addition, the torsion spring 55 is relaxed by rotating the adjusting gear 49 relative to the drive shaft 53 in a second direction of rotation opposite to the first direction of rotation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Claims (17)

  1. Procédé de fonctionnement d'une pompe à engrenages, un dispositif de refoulement avec au moins deux roues dentées (11, 13, 47, 49) disposées dans un boîtier (3) étant prévu, un liquide à refouler pouvant être refoulé à partir d'au moins une entrée de boîtier (5) vers au moins une sortie de boîtier (7) au moyen des roues dentées (11, 13, 47, 49), les roues dentées (11, 13, 47, 49), vues dans la direction axiale (x), étant disposées les unes derrière les autres, et un dispositif de réglage (21) étant prévu, au moyen duquel les roues dentées (11, 13, 47, 49) peuvent être tournées les unes par rapport aux autres et/ou déplacées les unes par rapport aux autres, de telle sorte qu'un dispositif de fixation (23) soit prévu, au moyen duquel au moins une roue dentée (11, 49) constituant une roue dentée de réglage peut être déplacée par rapport à au moins une autre roue dentée (13, 47) et/ou est fixée de manière rotative sur le boîtier (3), caractérisé en ce que les roues dentées (11, 13, 47, 49) sont tournées les unes par rapport aux autres et/ou déplacées les unes par rapport aux autres au moyen du dispositif de réglage (21) en fonction des rapports de pression à l'intérieur du boîtier (3), le dispositif de réglage (21) présentant au moins un élément de ressort en tant qu'élément de précontrainte (31) au moyen duquel la roue dentée de réglage (11, 49) peut être précontrainte dans une position de base.
  2. Procédé selon la revendication 1, caractérisé en ce que les roues dentées (11, 13, 47, 49) sont disposées dans le boîtier (3) de telle sorte que leurs axes de rotation soient orientés de manière essentiellement coïncidente ou parallèle les uns aux autres et/ou en ce que les roues dentées (11, 13, 47, 49) sont tournées axialement les unes par rapport aux autres et/ou déplacées dans la direction radiale les unes par rapport aux autres au moyen du dispositif de réglage (21) en fonction des rapports de pression à l'intérieur du boîtier (3).
  3. Procédé selon la revendication 1 ou 2, caractérisé en ce que les roues dentées (11, 13, 47, 49) présentent un contour extérieur radial essentiellement identique, en ce que les roues dentées (11, 13, 47, 49), dans la position de base, vues dans la direction axiale (x), sont disposées en alignement les unes par rapport aux autres, et en ce que si la contre-pression de liquide au niveau de la sortie de boîtier (7) passe en dessous d'au moins une valeur minimale définie, les roues dentées (11, 13, 47, 49) sont déplacées d'une position ne correspondant pas à la position de base au moyen du dispositif de réglage (21) dans la position de base.
  4. Procédé selon la revendication 3, caractérisé en ce que si la contre-pression de liquide au niveau de la sortie de boîtier (7) ne passe pas en dessous de l'au moins une valeur minimale, les roues dentées (11, 13, 47, 49) disposées dans la position de base sont tournées les unes par rapport aux autres et/ou déplacées les unes par rapport aux autres au moyen du dispositif de réglage (21).
  5. Procédé selon la revendication 4, caractérisé en ce que si la contre-pression de liquide au niveau de la sortie de boîtier (7) dépasse au moins une valeur maximale définie, supérieure à la valeur minimale, les roues dentées (11, 13, 47, 49) sont déplacées dans une position maximale dans laquelle les roues dentées (11, 13, 47, 49) sont disposées de manière tournée les unes par rapport aux autres de la moitié de leur pas de denture.
  6. Pompe à engrenages comprenant un dispositif de refoulement qui présente au moins deux roues dentées (11, 13, 47, 49) disposées dans un boîtier (3), un liquide à refouler pouvant être refoulé à partir d'au moins une entrée de boîtier (5) vers au moins une sortie de boîtier (7) au moyen des roues dentées (11, 13, 47, 49), les roues dentées (11, 13, 47, 49), vues dans la direction axiale (x), étant disposées les unes derrière les autres, et un dispositif de réglage (21) étant prévu, au moyen duquel les roues dentées (11, 13, 47, 49) peuvent être tournées les unes par rapport aux autres et/ou déplacées les unes par rapport aux autres, de telle sorte qu'un dispositif de fixation (23) soit prévu, au moyen duquel au moins une roue dentée (11, 49) constituant une roue dentée de réglage peut être déplacée par rapport à au moins une autre roue dentée (13, 47) et/ou est fixée de manière rotative sur le boîtier (3), caractérisée en ce que les roues dentées (11, 13, 47, 49) peuvent être tournées les unes par rapport aux autres et/ou déplacées les unes par rapport aux autres au moyen du dispositif de réglage (21) en fonction des rapports de pression à l'intérieur du boîtier (3), le dispositif de réglage (21) présentant au moins un élément de ressort en tant qu'élément de précontrainte (31) au moyen duquel la roue dentée de réglage (11, 49) peut être précontrainte dans une position de base.
  7. Pompe à engrenages selon la revendication 6, caractérisée en ce que l'élément de précontrainte (31) est formé par un ressort de torsion.
  8. Pompe à engrenages selon la revendication 6 ou 7, caractérisée en ce que l'élément de précontrainte (31) coopère avec une butée (41), en particulier avec au moins un élément de butée qui empêche une rotation et/ou un déplacement de la roue dentée de réglage (11, 49) disposée dans la position de base dans au moins une direction définie.
  9. Pompe à engrenages selon l'une quelconque des revendications 6 à 8, caractérisée en ce que la roue dentée de réglage (11, 49) disposée dans la position de base se déplace et/ou tourne par rapport à l'au moins une autre roue dentée (13, 47) en cas de rapports de pression définis dans le boîtier (3), et en ce que l'élément de précontrainte (31) peut être tendu par ce déplacement et/ou cette rotation de la roue dentée de réglage (11, 49) en développant une force de rappel.
  10. Pompe à engrenages selon l'une quelconque des revendications 6 à 9, caractérisée en ce qu'un élément de butée (43) est prévu, au moyen duquel le déplacement et/ou la rotation de la roue dentée de réglage (13, 47) disposée dans la position de base peuvent être limités.
  11. Pompe à engrenages selon l'une quelconque des revendications 6 à 10, caractérisée en ce que la pompe à engrenages est réalisée sous forme de pompe à engrenages intérieurs (1), les au moins deux roues dentées (11, 13) étant formées par des roues dentées à denture extérieure qui sont en engagement denté avec au moins un élément de roue dentée à denture intérieure (9).
  12. Pompe à engrenages selon la revendication 11, caractérisée en ce que le dispositif de fixation (23) présente un élément de fixation (25) au moyen duquel la roue dentée de réglage (11) est fixée au boîtier (3) de manière à pouvoir être déplacée par rapport au boîtier (3), la roue dentée de réglage (11) étant fixée de manière rotative sur l'élément de fixation (25) en constituant un premier axe de rotation (A1), l'élément de fixation (25) étant fixé de manière rotative au boîtier (3) en constituant un deuxième axe de rotation (A2) disposé essentiellement parallèlement au premier axe de rotation (A1), et la roue dentée de réglage (11) pouvant être déplacée par rotation de l'élément de fixation (25) par rapport au boîtier (3), l'élément de fixation (25) étant de préférence prévu pour être réalisé essentiellement en forme de Z.
  13. Pompe à engrenages selon la revendication 12, caractérisée en ce que l'élément de précontrainte (31) peut être tendu par rotation de l'élément de fixation (25) dans un premier sens de rotation (R1) et en ce que l'élément de précontrainte (31) peut être détendu par rotation de l'élément de fixation (25) dans un deuxième sens de rotation (R2) opposé au premier sens de rotation (R1), l'élément de précontrainte (31) étant de préférence prévu pour être fixé par une région d'extrémité (33) à une région (35) de l'élément de fixation (25) faisant saillie hors du boîtier (3).
  14. Pompe à engrenages selon l'une quelconque des revendications 6 à 10, caractérisée en ce que la pompe à engrenages est réalisée sous forme de pompe à engrenages extérieurs (45), les au moins deux roues dentées (47, 49) étant formées par des roues dentées à denture extérieure et constituant les roues dentées d'entraînement pour l'entraînement de la pompe à engrenages extérieurs (45) et chacune de ces roues dentées d'entraînement (47, 49) étant à chaque fois en engagement denté avec une roue dentée à denture extérieure correspondante (51).
  15. Pompe à engrenages selon la revendication 14, caractérisée en ce que le dispositif de fixation (23) présente un arbre d'entraînement (53) fixé de manière rotative sur le boîtier (3) pour l'entraînement des roues dentées d'entraînement (47, 49), au moins une roue dentée d'entraînement (47) étant connectée de manière solidaire en rotation à l'arbre d'entraînement (53), au moins une roue dentée d'entraînement (49) constituant la roue dentée de réglage étant fixée de manière rotative axialement par rapport à l'arbre d'entraînement (53) sur l'arbre d'entraînement (53), et les roues dentées d'entraînement (47, 49) étant connectées au moyen de l'élément de précontrainte (31) avec transmission de couple.
  16. Pompe à engrenages selon la revendication 15, caractérisée en ce que l'élément de précontrainte (31) peut être tendu par rotation de la roue dentée de réglage (49) par rapport à l'arbre d'entraînement (53) dans un premier sens de rotation, et en ce que l'élément de précontrainte (31) peut être détendu par rotation de la roue dentée de réglage (49) par rapport à l'arbre d'entraînement (53) dans un deuxième sens de rotation opposé au premier sens de rotation.
  17. Véhicule comprenant une pompe à engrenages selon l'une quelconque des revendications 6 à 16.
EP15002727.4A 2015-02-03 2015-09-22 Procede de fonctionnement d'une pompe à engrenages et pompe à engrenages Active EP3054161B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102015001235.5A DE102015001235A1 (de) 2015-02-03 2015-02-03 Verfahren zum Betreiben einer Zahnradpumpe und Zahnradpumpe

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EP3054161A1 EP3054161A1 (fr) 2016-08-10
EP3054161B1 true EP3054161B1 (fr) 2020-07-15

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US (1) US10436082B2 (fr)
EP (1) EP3054161B1 (fr)
CN (1) CN105840499B (fr)
BR (1) BR102015030185B1 (fr)
DE (1) DE102015001235A1 (fr)
RU (1) RU2699859C2 (fr)

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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
GB2592623B (en) * 2020-03-04 2024-09-11 Phinia Delphi Luxembourg Sarl A pump assembly
RU199143U1 (ru) * 2020-04-22 2020-08-19 Публичное акционерное общество «Авиационная корпорация «Рубин» Героторный насос

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DE1231563B (de) * 1963-01-16 1966-12-29 Danfoss As Regelbare Zahnradpumpe
GB8707127D0 (en) * 1987-03-25 1987-04-29 Blything W C Hydraulic transmission
CH679062A5 (fr) * 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
GB2313411B (en) * 1996-05-25 1999-10-13 Concentric Pumps Ltd Improvements in drive systems
DE19746768C2 (de) 1997-10-23 2001-06-21 Bosch Gmbh Robert Zahnradmaschine
DE10334954A1 (de) * 2003-07-31 2005-02-24 Voith Turbo Gmbh & Co. Kg Hydropumpe
RU2376498C2 (ru) * 2004-12-30 2009-12-20 Владислав Анатольевич Власенков Роторно-поршневая регулируемая гидромашина
GB2430237A (en) 2005-06-11 2007-03-21 Concentric Pumps Ltd Variable output internal gear pump
GB0620648D0 (en) * 2006-10-18 2006-11-29 Concentric Vfp Ltd Improvements in gerotor pump performance
GB0620646D0 (en) 2006-10-18 2006-11-29 Concentric Vfp Ltd Pumps with filling slots
ITBO20080686A1 (it) 2008-11-13 2010-05-14 Cnh Italia Spa Pompa di tipo gerotor
CN102536795A (zh) * 2011-12-27 2012-07-04 张意立 一种锥形弹簧补偿齿轮泵
DE102012009605A1 (de) * 2012-05-15 2013-11-21 Man Truck & Bus Ag Verfahren zur Kompensation einer Achsabstandsänderung am Steuertrieb einer ventilgesteuerten Brennkraftmaschine sowie Steuertrieb für eine ventilgesteuerte Brennkraftmaschine

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Also Published As

Publication number Publication date
EP3054161A1 (fr) 2016-08-10
RU2015146371A (ru) 2017-05-04
RU2699859C2 (ru) 2019-09-11
US20160230620A1 (en) 2016-08-11
CN105840499A (zh) 2016-08-10
US10436082B2 (en) 2019-10-08
BR102015030185B1 (pt) 2022-11-16
DE102015001235A1 (de) 2016-08-04
BR102015030185A2 (pt) 2016-10-04
CN105840499B (zh) 2020-06-26
RU2015146371A3 (fr) 2019-03-07

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