EP3728850B1 - Dispositif de transport de fluide - Google Patents

Dispositif de transport de fluide Download PDF

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Publication number
EP3728850B1
EP3728850B1 EP18829267.6A EP18829267A EP3728850B1 EP 3728850 B1 EP3728850 B1 EP 3728850B1 EP 18829267 A EP18829267 A EP 18829267A EP 3728850 B1 EP3728850 B1 EP 3728850B1
Authority
EP
European Patent Office
Prior art keywords
pump
fluid
main pump
gear
main
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
EP18829267.6A
Other languages
German (de)
English (en)
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EP3728850A1 (fr
Inventor
Reinhard Pippes
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.)
Eckerle Technologies GmbH
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Eckerle Technologies GmbH
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Filing date
Publication date
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Publication of EP3728850A1 publication Critical patent/EP3728850A1/fr
Application granted granted Critical
Publication of EP3728850B1 publication Critical patent/EP3728850B1/fr
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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
    • 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
    • F04C11/005—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle
    • 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
    • F04C14/24—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C14/26—Control of, monitoring of, or safety arrangements for, machines, pumps or pumping installations characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • 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
    • F04C2/101—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 with a crescent-shaped filler element, located between the inner and outer intermeshing 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
    • 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
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts

Definitions

  • the invention relates to a fluid delivery device with a backing pump and a main pump fluidically connected to the backing pump, the backing pump being drivable via a backing pump input shaft and the main pump being drivable via a main pump input shaft.
  • the object of the invention is to propose a fluid delivery device which has advantages over known fluid delivery devices, in particular an ideal coordination of the backing pump and the main pump with one another and consequently a long service life of the fluid delivery device, especially the main pump.
  • the backing pump has a backing pump drive wheel coupled to the backing pump input shaft and a backing pump delivery wheel that interacts with the backing pump drive wheel for fluid delivery, the backing pump and the main pump being drive-coupled to a common drive shaft, and the backing pump delivery wheel and the main pump input shaft being connected to one another via a connecting shaft are connected so that the foreline pump input shaft is coupled directly and the main pump input shaft is coupled to the drive shaft via the connecting shaft.
  • the fluid delivery device serves to deliver a fluid, for example a liquid or a gas.
  • the fluid delivery device has the backing pump and the main pump, the main pump being fluidically connected to the backing pump. That means, that the fluid is first fed to the backing pump, which conveys the fluid in the direction of the main pump.
  • the fluid delivered by the backing pump is thus made available to the main pump, which delivers the fluid further, namely, for example, in the direction of a fluid outlet of the fluid delivery device, which can also be referred to as a delivery device fluid outlet.
  • Each of the pumps has an input shaft via which it can be driven, namely the backing pump via the backing pump input shaft and the main pump via the main pump input shaft.
  • the backing pump also has two wheels for pumping fluid, namely the backing pump drive wheel and the backing pump delivery wheel.
  • the backing pump drive wheel and the backing pump feed wheel are provided for pumping fluid and for this reason are designed in such a way that when the fore pump input shaft rotates, they interact to deliver the fluid and, for example, intervene in one another.
  • the foreline drive gear is coupled to the foreline input shaft, preferably rigidly and / or permanently.
  • the backing pump drive wheel is preferably arranged on the backing pump input shaft so that it always has the same speed as the backing pump input shaft during operation of the backing pump.
  • the backing pump input shaft is coupled in terms of drive technology to the common drive shaft, preferably in turn rigidly and / or permanently.
  • the backing pump input shaft and the common drive shaft are designed in one piece, so that the backing pump input shaft is formed from the drive shaft and / or vice versa. In this respect, the backing pump can be driven directly and immediately via the drive shaft.
  • the main pump should only be drivable indirectly via the drive shaft.
  • the main pump is connected in terms of drive technology to the drive shaft via the backing pump, so that when the drive shaft rotates, the main pump is driven via the backing pump.
  • the backing pump drive wheel and the backing pump feed wheel are connected to one another in terms of drive technology. This means that the backing pump drive wheel is provided and configured for driving the backing pump feed wheel, so that when the backing pump input shaft rotates, both the backing pump drive wheel and the backing pump feed wheel are rotated.
  • the backing pump impeller is now connected in terms of drive technology to the main pump input shaft, namely via the connecting shaft.
  • the main pump is with the foreline pump impeller Connected in terms of drive technology, so that there is preferably also a rotary movement of the main pump input shaft when the backing pump impeller is rotated.
  • the main pump input shaft and the connecting shaft can be configured separately or in one piece with one another. In the latter case, the main pump input shaft forms the connecting shaft and / or vice versa.
  • the backing pump impeller is rotatably mounted by means of the connecting shaft and / or the main pump input shaft.
  • the fluid delivery device is designed in such a way that the backing pump input shaft is coupled directly and immediately to the drive shaft.
  • the main pump input shaft is only indirectly coupled to the drive shaft via the connecting shaft and / or the backing pump.
  • Such a configuration of the fluid delivery device has the advantage that the speed of the backing pump and the main pump or the respective input shaft are in a fixed relationship with one another, so that, for example, there is a certain ratio between the speeds. This achieves very good coordination between the backing pump and the main pump during the operation of the fluid delivery device.
  • Another embodiment of the invention provides that the backing pump drive wheel and the backing pump feed wheel form a transmission gear for the main pump with a specific transmission ratio.
  • the specific transmission ratio exists between the fore pump drive wheel and the fore pump feed wheel and therefore also between the fore pump input shaft and / or the drive shaft on the one hand and the connecting shaft and / or main pump input shaft on the other.
  • the transmission ratio is preferably different from one, so that due to the transmission gear during operation of the fluid delivery device, the fore pump impeller has a speed which is different from a speed of the fore pump drive wheel or a certain speed ratio exists between the speed of the fore pump impeller and the speed of the fore pump drive wheel, which corresponds to the transmission ratio is equivalent to.
  • the speed of the drive shaft for the main pump is adjusted with the aid of the backing pump.
  • an optimal speed can be achieved for both the backing pump and the main pump without having to provide an additional gear via which the backing pump input shaft and the main pump input shaft are connected to one another are.
  • by driving the main pump via the backing pump a particularly compact design of the fluid delivery device is implemented.
  • the backing pump is designed as a gear pump and / or the main pump is designed as a rotary piston pump.
  • the configuration of the backing pump as a gear pump enables a particularly advantageous and reliable use of the backing pump as a transmission gear.
  • the gear pump is understood to mean, for example, an external gear pump or an internal gear pump.
  • the backing pump or the gear pump is particularly preferably gap-compensated. If the backing pump is in the form of a gear pump, the backing pump drive gear can be referred to as the backing pump drive gear and the backing pump conveying gear can be referred to as the backing pump conveying gear and, according to their designation, are present as gears.
  • the interaction of the gears for fluid delivery takes place by engaging with one another or by meshing with one another.
  • the forepump drive gear meshes with the forepump feed gear for fluid delivery, the transmission gear being formed at the same time.
  • a toothing of the backing pump drive gear and a toothing of the backing pump delivery gear are preferably designed as helical gears. As a result, noise from the backing pump can be significantly reduced compared to straight teeth.
  • the toothing can alternatively also be designed as straight toothing.
  • the main pump is a rotary piston pump.
  • the rotary piston pump is understood to mean, for example, a rotary piston pump, a rotary vane pump, a rotary piston pump or a gear pump.
  • the gear pump can in turn be designed as an external gear pump and as an internal gear pump.
  • the main pump is also particularly preferably designed to be gap-compensated, namely in particular in the case of its design as a gear pump.
  • the main pump is particularly preferably designed as a gear pump, that is to say, for example, as an external gear pump or as an internal gear pump, the latter being the case in the context of a particularly preferred embodiment of the fluid delivery device.
  • the backing pump and the main pump being designed as gear pumps, so that both pumps are therefore each in the form of a gear pump.
  • the backing pump is designed as an external gear pump and the main pump as an internal gear pump. A particularly reliable provision of the fluid for the main pump by the backing pump is thereby achieved.
  • the backing pump has a larger delivery volume than the main pump.
  • the delivery volume can also be referred to as the displacement volume.
  • the delivery volume of the backing pump is at least 5%, at least 10%, at least 15%, at least 20% or at least 25% greater than the delivery volume of the main pump.
  • a further embodiment of the invention provides that the main pump has a main pump drive wheel and a main pump feed wheel interacting with the main pump drive wheel for fluid delivery, the backing pump feed wheel and the main pump drive wheel being drive-connected to the connecting shaft.
  • the main pump drive wheel also interacts with the main pump feed wheel to convey fluid, for example by engaging or meshing with one another. If the main pump is designed as a gear pump, the main pump drive gear can be referred to as the main pump drive gear and the main pump feed gear can be referred to as the main pump feed gear.
  • the main pump drive wheel is drive-coupled to the main pump input shaft, preferably rigidly and / or permanently.
  • the main pump drive wheel is seated on the main pump input shaft, so that when the fluid delivery device is in operation, the speed of the main pump drive wheel corresponds to the speed of the main pump input shaft.
  • the main pump drive wheel and the main pump feed wheel cooperate to convey fluid in such a way that the main pump feed wheel is driven by the main pump drive wheel during operation of the fluid feed device.
  • a rotary movement of the main pump drive wheel there is also a rotary movement of the main pump feed wheel, as a result of which the fluid feed effect is achieved overall.
  • the backing pump delivery wheel and the main pump drive wheel are connected to the connecting shaft in terms of drive technology, namely preferably rigidly and / or permanently.
  • the connecting shaft is designed in one piece with the main pump input shaft or forms it.
  • Both the backing pump impeller and the are preferred Main pump drive wheel arranged on the connecting shaft and connected to it in terms of drive technology.
  • the foreline pump impeller and the main pump drive wheel are rotatably supported by the connecting shaft. This avoids additional mounting of the backing pump delivery wheel or the main pump drive wheel, so that the space requirement of the fluid delivery device is further reduced.
  • the main pump is an internal gear pump, in particular a sickle pump, the main pump drive gear being configured as a pinion gear and the main pump delivery gear being configured as a ring gear.
  • the internal gear pump is particularly preferably designed to be gap-compensated.
  • the internal gear pump can be designed without a filler piece, that is to say without a filler piece, or with a filler piece.
  • the sickle pump in which the (sickle-shaped) filler piece is arranged between the pinion gear and the ring gear, so that the filler piece - seen in cross section with respect to an axis of rotation of the pinion gear and / or an axis of rotation of the main pump impeller - with an in inner side located radially inward on the pinion gear, in particular on teeth of the pinion gear, and with its side located on the outside in radial direction on the ring gear, in particular on teeth of the ring gear.
  • the design of the main pump as an internal gear pump enables the fluid delivery device to be particularly efficient.
  • a further transmission gear is arranged in the operative connection between the backing pump delivery wheel and the main pump input shaft.
  • the further step-up gear is added to the step-up gear formed by the backing pump drive wheel and the backing-pump feed wheel, so that the main pump is connected to the drive shaft via the step-up gear and the further step-up gear, which are connected in series with one another.
  • the further transmission gear is present, for example, as a gear transmission, for example as a spur gear transmission. In particular, it is designed as a planetary gear or planetary gear.
  • the further transmission gear has a transmission ratio which is preferably different from one, so that there is a certain speed ratio between the speed of the main pump input shaft and the speed of the backing pump impeller, which corresponds to the transmission ratio of the further transmission gear.
  • the speeds of the backing pump delivery wheel and the main pump input shaft are during operation of the fluid delivery device different from each other.
  • the use of the further transmission gear enables both the backing pump and the main pump to operate at an optimal speed in each case.
  • the invention provides that the backing pump has a backing pump fluid inlet and a backing pump fluid outlet, and the main pump has a main pump fluid inlet and a main pump fluid outlet, a delivery device fluid inlet of the fluid delivery device being connected to the backing pump fluid inlet, the backing pump fluid outlet being fluidly connected to the main pump fluid inlet and the main pump fluid inlet and the main pump fluid inlet.
  • the fluid delivery device itself thus has the delivery device fluid inlet and the delivery device fluid outlet.
  • the fluid is provided to the fluid delivery device via the delivery device fluid inlet, and the fluid delivered by means of the backing pump and the main pump is provided through the delivery device fluid outlet. In other words, fluid is supplied to the fluid delivery device via the delivery device fluid inlet and fluid is withdrawn via the delivery device fluid outlet.
  • the foreline pump has the foreline fluid inlet and the foreline fluid outlet.
  • the backing pump is provided with fluid via the backing pump fluid inlet and the fluid conveyed by means of the backing pump is withdrawn via the backing pump fluid outlet.
  • the main pump is provided with the fluid via the main pump fluid outlet, which fluid is withdrawn through the main pump fluid outlet after it has been conveyed by the main pump.
  • the backing pump and the main pump are fluidically connected in series.
  • the backing pump fluid inlet is fluidically connected to the delivery device fluid inlet, so that the fluid that is fed to the fluid delivery device is fed directly to the backing pump.
  • the backing pump fluid outlet is connected to the main pump inlet, so that the main pump is provided with fluid delivered by means of the backing pump.
  • the main pump fluid outlet in turn, is fluidically connected to the delivery device fluid outlet, so that the fluid delivered by means of the backing pump and the main pump is or can be removed via the delivery device fluid outlet of the fluid delivery device.
  • the invention provides that the backing pump fluid outlet is fluidically connected to the backing pump fluid inlet via a bypass line having a check valve.
  • fluid can flow back via the bypass line from the backing pump fluid outlet to the backing pump fluid inlet, bypassing the backing pump.
  • the valve arrangement by means of which the flow connection can be adjusted, is arranged in the bypass line. For example, in a first setting of the valve arrangement, the flow connection between the fore-pump fluid outlet and the fore-pump fluid inlet via the bypass line is interrupted, whereas it is established in a second setting.
  • the valve arrangement is particularly preferably in the form of the check valve or at least has one. This is designed in such a way that it allows a flow from the fore-pump fluid outlet to the fore-pump fluid inlet, but prevents a flow in the opposite direction.
  • the check valve is designed in such a way that it only establishes the flow connection between the fore pump fluid outlet and the fore pump fluid inlet in the direction of the fore pump fluid inlet when a pressure difference between the fore pump fluid outlet and the fore pump fluid inlet exceeds a certain pressure difference.
  • the check valve acts in particular as a pressure limiting valve, so that the pressure applied to the main pump on the inlet side and caused by the backing pump is limited to a specific value.
  • bypass line and the check valve or pressure relief valve are used to supply the main pump with fluid as required. They are particularly necessary if, in at least one operating state, the backing pump conveys more fluid in the direction of the main pump than it can absorb.
  • An embodiment is therefore particularly ideal in which the bypass line and the valve arrangement or the non-return valve are omitted and the backing pump is matched to the main pump in such a way that the fluid is always ideally applied to the main pump.
  • the backing pump of the main pump provides exactly or at least almost exactly the amount of fluid that it can take up, in particular at exactly one speed of the drive shaft, at least one speed of the drive shaft or several different speeds of the drive shaft, particularly preferably over a nominal speed range of the drive shaft, which occurs or at least can occur during normal operation of the fluid delivery device.
  • the backing pump and the main pump are arranged in a common pump housing.
  • the two pumps that is to say the backing pump and the main pump, are therefore not present in different housings, but rather are integrated in the fluid delivery device.
  • both the backing pump drive wheel and the backing pump feed wheel of the backing pump and the main pump drive wheel and the main pump feed wheel of the main pump are rotatably mounted in or on the common pump housing. This results in a particularly compact design of the fluid delivery device.
  • the Figure 1 shows a schematic representation of a fluid delivery device 1, which has a backing pump 2 and a main pump 3.
  • the backing pump 2 has a backing pump fluid inlet 4, which is fluidically connected to a delivery device fluid inlet 5.
  • a backing pump fluid outlet 6 of the backing pump 2 is fluidically connected to a main pump fluid inlet 7.
  • the backing pump 2 and the main pump 3 are connected in series in terms of flow between the delivery device fluid inlet 5 and the delivery device fluid outlet 9.
  • the foreline fluid outlet 6 and the foreline fluid inlet 4 are fluidically connected to one another via a bypass line 10.
  • a valve arrangement 11 is provided which has a check valve 12 or is designed as such.
  • the backing pump 2 can be driven via a backing pump input shaft 13 and the main pump 3 via a main pump input shaft 14.
  • the backing pump 2 and the main pump 3 are drive-connected to a common drive shaft 15.
  • the backing pump input shaft 13 and the main pump input shaft 14 are both connected to the drive shaft 15 in terms of drive technology.
  • the backing pump input shaft 13 there is a direct connection.
  • the backing pump input shaft 13 is formed in one piece with the drive shaft 15.
  • the main pump input shaft 14, on the other hand, is drive-connected to the drive shaft 15 via the backing pump 2.
  • a backing pump drive wheel 16 and a backing pump feed wheel 17 of the backing pump 2 form a transmission gear 18 for the main pump 3.
  • the backing pump drive wheel 16 is coupled to the backing pump input shaft 13, preferably it sits on this and is rigidly and / or permanently connected to it.
  • the backing pump delivery wheel 17, is driven by the backing pump drive wheel 16 during operation of the fluid delivery device 1, that is to say when the drive shaft 15 is rotating.
  • the backing pump 2 is a gear pump, namely an external gear pump.
  • the backing pump drive wheel 16 and the backing pump feed wheel 17 are provided as gear wheels which mesh with one another to form the transmission gear 18.
  • the backing pump drive wheel 16 and the backing pump feed wheel 17 work together to convey fluid.
  • the main pump 3 has a main pump drive wheel 19 and a main pump delivery wheel 20. These also work together to provide a fluid delivery effect of the main pump 3.
  • a connecting shaft 21 is provided which connects the backing pump feed wheel 17 and the main pump input shaft 14 and therefore the main pump drive wheel 19 to one another.
  • the backing pump input shaft 13 is directly coupled to the drive shaft 15, whereas the main pump input shaft 14 is only indirectly coupled to the drive shaft 15 via the connecting shaft 21 and the backing pump 2, i.e. is driven by the drive shaft 15 via the backing pump 2.
  • a configuration of the fluid delivery device 1 in which both the backing pump 2 and the main pump 3 are configured as gear pumps is particularly advantageous.
  • the backing pump 2 is an external gear pump and the main pump 3 is an internal gear pump.
  • the main pump drive wheel 19 represents a pinion gear 22 and the main pump feed wheel 20 represents a ring gear 23 of the internal gear pump.
  • the pinion gear 22 and the ring gear 23 are rotatably mounted about axes of rotation that are offset parallel to one another.
  • the pinion gear 2 has outer dimensions which are smaller than the inner dimensions of the ring gear 23, so that only part of a toothing of the pinion gear 22 meshes with a toothing of the ring gear 23.
  • the internal gear pump is designed as a sickle pump, so that a sickle-shaped filler piece 24 is arranged in some areas between the pinion gear 22 and the ring gear 23.
  • Either the backing pump 2 or the main pump 3 are preferably designed to be gap-compensated.
  • the main pump 3, but not the backing pump 2 is gap-compensated.
  • the backing pump 2 is present without any gap compensation.
  • both the backing pump 2 and the main pump 3 can also be gap-compensated.
  • the Figure 2 shows a further schematic representation of the fluid delivery device 1. It can be seen that the backing pump 2 or the backing pump drive wheel 16 and the backing pump feed wheel 17 each have helical teeth. This significantly improves the running smoothness of the backing pump 2. With regard to the further configuration of the fluid delivery device 1, reference is made to the above statements.
  • the Figure 3 shows a further schematic representation of the fluid delivery device 1.
  • the backing pump 2 and the main pump 3 are arranged in a common pump housing 25.
  • the fore pump drive wheel 16, the fore pump feed wheel 17, the main pump drive wheel 19 and the main pump feed wheel 20 are preferably rotatably mounted in and / or on the pump housing 25.
  • a direction of flow of the fluid through the fluid delivery device 1 is indicated by the arrows 26.
  • the fluid delivery device 1 shown here has excellent delivery properties for the fluid with a long service life because the backing pump 2 and the main pump 3 are ideally matched to one another, namely by means of the transmission gear 18.

Claims (7)

  1. Dispositif de transport de fluide (1) comprenant une pompe préliminaire (2) et une pompe principale (3) en liaison fluidique avec la pompe préliminaire (2), la pompe préliminaire (2) pouvant être entraînée par le biais d'un arbre d'entrée de pompe préliminaire (13) et la pompe principale (3) par le biais d'un arbre d'entrée de pompe principale (14), et la pompe préliminaire (2) comportant une entrée de fluide de pompe préliminaire (4) et une sortie de fluide de pompe préliminaire (6) et la pompe principale (3) une entrée de fluide de pompe principale (7) et une sortie de fluide de pompe principale (8), une entrée de fluide de dispositif de transport (5) du dispositif de transport de fluide (1) étant en liaison fluidique avec l'entrée de fluide de pompe préliminaire (4), la sortie de fluide de pompe préliminaire (6) avec l'entrée de fluide de pompe principale (7) et la sortie de fluide de pompe principale (8) avec la sortie de fluide de dispositif de transport (9) du dispositif de transport de fluide (1), caractérisé en ce que la pompe préliminaire (2) dispose d'une roue d'entraînement de pompe préliminaire (16) couplée à l'arbre d'entrée de pompe préliminaire (13) et d'une roue de transport de pompe préliminaire (17) coopérant avec la roue d'entraînement de pompe préliminaire (16) pour le transport de fluide, la pompe préliminaire (2) et la pompe principale (3) étant couplées selon une technique d'entraînement à un arbre d'entraînement (15) commun, et la roue de transport de pompe préliminaire (17) et l'arbre d'entrée de pompe principale (14) étant reliés l'un à l'autre par un arbre de liaison (21), de telle sorte que l'arbre d'entrée de pompe préliminaire (13) est couplé directement à l'arbre d'entraînement (15) et l'arbre d'entrée de pompe principale (14) par le biais de l'arbre de liaison (21), la sortie de fluide de pompe préliminaire (6) étant en liaison fluidique avec l'entrée de fluide de pompe préliminaire (4) par le biais d'une ligne de dérivation (10) comportant un clapet antiretour (12) et la pompe préliminaire (2) présentant un volume transporté supérieur à la pompe principale (3).
  2. Dispositif de transport de fluide selon la revendication 1, caractérisé en ce que la roue d'entraînement de pompe préliminaire (16) et la roue de transport de pompe préliminaire (17) forment un engrenage multiplicateur (18) pour la pompe principale (3) avec un rapport de multiplication donné.
  3. Dispositif de transport de fluide selon l'une des revendications précédentes, caractérisé en ce que la pompe préliminaire (2) est réalisée sous la forme d'une pompe à engrenages et/ou la pompe principale (3) sous la forme d'une pompe à pistons rotative.
  4. Dispositif de transport de fluide selon l'une des revendications précédentes, caractérisé en ce que la pompe principale (3) comporte une roue d'entraînement de pompe principale (19) et une roue de transport de pompe principale (20) coopérant avec la roue d'entraînement de pompe principale (19) pour le transport de fluide, la roue de transport de pompe préliminaire (17) et la roue d'entraînement de pompe principale (19) étant reliées selon une technique d'entraînement à l'arbre de liaison (21).
  5. Dispositif de transport de fluide selon l'une des revendications précédentes, caractérisé en ce que la pompe principale (3) se présente sous la forme d'une pompe à engrenages intérieurs, en particulier d'une pompe à tambour en forme de croissant, la roue d'entraînement de pompe principale (19) étant conçue sous la forme d'un pignon (22) et la roue de transport de pompe principale (20) sous la forme d'une roue à denture intérieure (23).
  6. Dispositif de transport de fluide selon l'une des revendications précédentes, caractérisé en ce qu'un autre engrenage multiplicateur est disposé dans la liaison fonctionnelle entre la roue de transport de pompe préliminaire (17) et l'arbre d'entrée de pompe principale (14).
  7. Dispositif de transport de fluide selon l'une des revendications précédentes, caractérisé en ce que la pompe préliminaire (2) et la pompe principale (3) sont disposées dans un corps de pompe (25) commun.
EP18829267.6A 2017-12-22 2018-12-13 Dispositif de transport de fluide Active EP3728850B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017223675.2A DE102017223675B4 (de) 2017-12-22 2017-12-22 Fluidfördereinrichtung
PCT/EP2018/084721 WO2019121307A1 (fr) 2017-12-22 2018-12-13 Dispositif de transport de fluide

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EP3728850A1 EP3728850A1 (fr) 2020-10-28
EP3728850B1 true EP3728850B1 (fr) 2021-10-27

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US (1) US11248602B2 (fr)
EP (1) EP3728850B1 (fr)
CN (1) CN111566349B (fr)
DE (1) DE102017223675B4 (fr)
WO (1) WO2019121307A1 (fr)

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DE4439545A1 (de) 1994-11-05 1996-05-09 Gerhard Hestermann Vorrichtung zur teilweisen Trennung flüssiger Lösungen nach dem Prinzip der Querfiltration
US5820354A (en) * 1996-11-08 1998-10-13 Robbins & Myers, Inc. Cascaded progressing cavity pump system
KR100449312B1 (ko) * 1996-11-11 2004-11-26 라필찬 쌍원통임펠러형펌프
JP3760298B2 (ja) * 1998-07-29 2006-03-29 株式会社日立製作所 複合型ギヤポンプ
US6679692B1 (en) * 2002-07-12 2004-01-20 James J. Feuling Oil pump
JP2006161616A (ja) 2004-12-03 2006-06-22 Hitachi Ltd タンデム型トロコイドポンプおよびその組み付け方法
BRPI0716188A2 (pt) * 2006-09-08 2013-11-12 Hybra Drive Systems Llc Dispositivo de motor/bomba de tipo telescópico
DE102007032103B4 (de) 2007-05-16 2022-02-24 Robert Bosch Gmbh Pumpeneinheit mit einer Hauptpumpe und einer in ihrem Fördervolumen verstellbaren Ladepumpe
WO2011076172A2 (fr) * 2009-12-21 2011-06-30 Schaeffler Technologies Gmbh & Co. Kg Commande hydraulique
JP6129483B2 (ja) * 2012-04-19 2017-05-17 株式会社ミクニ オイルポンプ
DE102012210925A1 (de) * 2012-06-27 2014-05-15 Robert Bosch Gmbh Doppelinnenzahnradpumpe
DE102012112720B4 (de) 2012-12-20 2017-01-12 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Pumpe
DE102013223860A1 (de) * 2013-11-21 2015-05-21 Robert Bosch Gmbh Innenzahnradpumpe
FR3022951B1 (fr) 2014-06-26 2020-01-24 Safran Aircraft Engines Pompe a deux etages, prevue notamment comme pompe principale d'alimentation d'un moteur d'avion en carburant

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DE102017223675A1 (de) 2019-06-27
US20200318635A1 (en) 2020-10-08
CN111566349B (zh) 2022-09-02
EP3728850A1 (fr) 2020-10-28
US11248602B2 (en) 2022-02-15
DE102017223675B4 (de) 2023-01-26
WO2019121307A1 (fr) 2019-06-27
CN111566349A (zh) 2020-08-21

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