EP3827170A1 - Dispositif de refoulement de fluide - Google Patents

Dispositif de refoulement de fluide

Info

Publication number
EP3827170A1
EP3827170A1 EP19744680.0A EP19744680A EP3827170A1 EP 3827170 A1 EP3827170 A1 EP 3827170A1 EP 19744680 A EP19744680 A EP 19744680A EP 3827170 A1 EP3827170 A1 EP 3827170A1
Authority
EP
European Patent Office
Prior art keywords
pump
backing
backing pump
main
main pump
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.)
Pending
Application number
EP19744680.0A
Other languages
German (de)
English (en)
Inventor
Reinhard Pippes
Artur Bohr
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
Original Assignee
Eckerle Technologies GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Eckerle Technologies GmbH filed Critical Eckerle Technologies GmbH
Publication of EP3827170A1 publication Critical patent/EP3827170A1/fr
Pending legal-status Critical Current

Links

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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/005—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids 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
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F04C23/003—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle having complementary function
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D13/00—Pumping installations or systems
    • F04D13/12—Combinations of two or more pumps

Definitions

  • the invention relates to a fluid delivery device with a backing pump and a main pump connected to the backing pump in terms of flow, the backing pump being drivable via a front pump input shaft and the main pump via a main pump input shaft, and the backing pump input shaft and the main pump input shaft being mechanically coupled to a common drive shaft of the fluid delivery device.
  • the document DE 10 2007 032 103 Al is known from the prior art.
  • This relates to a pump unit with a main pump and a thread pump adjustable in its delivery volume.
  • a cam ring is seen before.
  • the cam ring is loaded with an actuating force that depends on the input pressure of the main pump.
  • the backing pump is designed as an uncompensated gear pump or as a centrifugal pump and the main pump as a compensated internal gear pump.
  • 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 connected to the backing pump in terms of flow. This means that the fluid is first fed to the backing pump, which pumps the fluid in the direction of the main pump.
  • the fluid conveyed by the backing pump is thus made available to the main pump, which conveys 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 the 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 fluid delivery, namely the backing pump pinion and the backing ring gear.
  • the backing pump pinion has external teeth and the backing pump internal gear has internal teeth.
  • the external toothing and the internal toothing mesh with each other in some areas, that is, they mesh with one another.
  • the Vorpum penritzel and the Vorpumpenhohlrad are provided for fluid delivery and for this reason designed such that they cooperate with a rotation of the backing pump input shaft for conveying the fluid and here, for example, engage or mesh with each other.
  • the backing pump pinion is coupled to the backing pump input shaft, preferably rigid and / or permanent.
  • the backing pump pinion 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 to the common drive shaft in terms of drive technology, preferably in turn rigid and / or permanent.
  • the backing pump input shaft and the common drive shaft are configured in one piece, so that the backing pump input shaft is formed by 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 has the main pump pinion and the main pump ring gear.
  • the main pump pinion has external teeth and the main pump ring gear has internal teeth.
  • the external toothing and the internal toothing intermesh with each other, that is, they mesh with one another.
  • the main pump pinion and the main pump ring gear are in turn provided for fluid delivery and configured in such a way that they act together when the main pump input shaft rotates to deliver the fluid and in this case, for example, engage or mesh with one another.
  • the main pump input shaft to be coupled in terms of drive technology, preferably rigidly and / or permanently, in a manner analogous to the pre-pump input shaft.
  • the pump input shaft and the common drive shaft are configured in one piece, so that the main pump input shaft is formed by the drive shaft and / or vice versa.
  • the main pump can be driven directly and immediately via the drive shaft.
  • both the pre-pump input shaft and the main pump input shaft are separated from the common drive shaft are formed.
  • the backing pump input shaft and the main pump input shaft are configured in one piece and / or in the same material, so that together they form the drive shaft. Accordingly, the backing pump input shaft and the main pump input shaft are arranged coaxially with one another. In such an embodiment, the backing pump and the main pump are always operated at the same speed.
  • the main pump can only be driven indirectly via the drive shaft.
  • the main pump is connected to the drive shaft via the backing pump, so that when the drive shaft rotates, the main pump is driven by the backing pump.
  • the backing pump pinion and the backing pump internal gear are preferably connected to one another in terms of drive technology. This is to be understood to mean that the backing pump pinion is provided and designed to drive the backing pump ring gear, so that when the backing pump input shaft rotates, both the backing pump pinion and the backing pump ring gear rotate.
  • the backing ring gear is now connected to the main pump input shaft in terms of drive technology, namely via a connecting shaft.
  • the main pump is connected in terms of drive technology to the pre-pump ring gear, so that preferably there is also a rotational movement of the main pump input shaft when the backing pump ring gear rotates.
  • 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 connection shaft and / or vice versa.
  • the backing pump internal gear is rotatably supported by means of the connecting shaft and / or the main pump input shaft.
  • the fluid delivery device in this embodiment is designed such that the backing pump input shaft is directly and directly coupled 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 rotational 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 relationship between the rotational speeds and the two pumps are operated at different rotational speeds. As a result, a very good coordination between the backing pump and the main pump is achieved during the operation of the fluid delivery device.
  • both pumps that is to say both the backing pump and the main pump, are configured as gear pumps, the backing pump preferably being present as an internal gear pump or as an external gear pump and the main pump as an internal gear pump.
  • the main pump is axially and / or radially compensated.
  • the backing pump is designed as a centrifugal pump and the main pump as an internal gear pump. Again, the main pump is axially and / or radially compensated.
  • the main pump is axially compensated and radially uncompensated, axially uncompensated and radially compensated, or both axially compensated and radially compensated.
  • Axial compensation is understood to mean that, seen in the axial direction with respect to the respective internal gear pump, an axial disk is arranged between the pinion and the ring gear of the internal gear pump.
  • the axial disk can be moved in the axial direction with little play. It is forced in the axial direction in the direction of the pinion and the ring gear during the operation of the respective gear pump or internal gear pump and is preferably at least temporarily, in particular continuously, against the pinion.
  • Such an axial disk is particularly preferably present in the axial direction on opposite sides of the pinion and the ring gear.
  • the axial disks are each arranged between the pinion and the ring gear on the one hand and a machine housing of the main pump on the other hand, that is to say on the end face of the rit zel and the ring gear. Insofar as only one axial disk is dealt with below, the explanations are always transferable to each of the several axial disks, as far as can be seen.
  • the axial disk is preferably mounted in a rotationally fixed manner in the machine housing. It can have a pressure field on its side facing away from the pinion and the ring gear and in this respect facing the machine housing, which is designed, for example, in the form of a depression in the axial disk.
  • the pressure field can be pressurized with fluid under pressure via a fluid channel which is formed in the machine housing.
  • the pressure field is fluidly connected to a pressure side of the gear pump or internal gear pump via the fluid channel.
  • the pressure field is pressurized via the fluid channel. strikes and correspondingly pushed the axial disk in the axial direction in the direction of the pinion and the ring gear, in particular pushed onto the pinion and the ring gear.
  • the radial compensation of the internal gear pump is provided.
  • the internal gear pump has a filler, which is arranged between the pinion and the ring gear as seen in ra dialer direction with respect to an axis of rotation of the pinion.
  • the filler serves for fluid-technical separation of a pressure side from a suction side of the internal gear pump or a pressure chamber from a suction chamber, which are also formed in the radial direction between the pinion and the ring gear.
  • the filler is designed in several parts and has a first filler part, which bears on the pinion and a second filler part, which bears on the ring gear.
  • the two filler parts are movable in the radial direction relative to one another and are designed such that the first filler part is pushed inwards in the radial direction towards the pinion and the second filler part in the radial direction outwards against the ring gear.
  • a pressure chamber lying in the radial direction between the first filler part and the second filler part is connected in terms of flow to the pressure side of the internal gear pump, so that the pressure chamber is pressurized during operation of the internal gear pump. Due to the pressurization, the two filler parts are pressurized in the radial direction, so that the first filler part is urged in the direction or towards the pinion and the second filler part on or in the direction of the ring gear. It is therefore preferably provided for the axial compensation and / or the radial compensation of the internal gear pump that this takes place as a function of a pressure on the pressure side of the internal gear pump.
  • the sealing effect achieved by means of the axial disk and / or the filler is therefore greater, the greater the pressure on the pressure side of the internal gear pump.
  • the main pump can be designed with axial compensation, with radial compensation or with both axial compensation and radial compensation.
  • the backing pump designed as a gear pump is partially uncompensated, that is, either axially uncompensated or radially uncompensated. It is particularly preferred both axially uncompensated and radially uncompensated.
  • the backing pump does not have the compensation that the main pump has. Is the If the main pump is axially compensated and radially uncompensated, the backing pump is axially uncompensated and radially compensated.
  • the backing pump is axially compensated and radially uncompensated. If the main pump is axially compensated and radially compensated, the backing pump is axially uncompensated and radially uncompensated.
  • a first gear wheel takes the place of the pinion and a second gear wheel which meshes with the first gear wheel for conveying the fluid takes the place of the ring gear.
  • the centrifugal pump can be designed as a radial pump, diagonal pump, side channel pump, peripheral wheel pump or axial pump. With such a configuration of the fluid delivery device, very high speeds of at least the backing pump, but preferably also the main pump, can be achieved, so that overall the fluid delivery device is designed for extremely high fluid throughputs.
  • a further embodiment of the invention provides that the backing pump configured as an internal gear pump has a backing pump pinion and a backing pump ring gear and the main pump has a main pump pinion and a main pump ring gear, wherein the backing pump pinion and the main pump pinion are arranged coaxially and the backing pump ring and the main pump ring gear are axially offset from one another.
  • the designs for the main pump can of course also be used for the backing pump designed as a centrifugal pump.
  • the backing pump sprocket is rotatably mounted about a backing pump pinion axis of rotation, the backing pump ring gear around a backing pump ring gear axis, the main pump pinion about a main pump pinion rotation axis and the main pump hollow wheel about a main pump ring gear rotation axis.
  • the axes of rotation of the pinion and the ring gear of both the backing pump and the main pump are offset from one another so that their axes of rotation are spaced parallel to one another.
  • An embodiment of the fluid delivery device is preferred in which the backing pump pinion and the main pump pinion are arranged coaxially with one another, so that their axes of rotation coincide or are identical.
  • the backing pump ring gear and the main pump ring gear are to be arranged axially offset from one another, so that the backing pump ring gear axis of rotation and the main pump ring gear rotation axis are spaced apart in parallel. This enables a particularly advantageous fluid flow between the backing pump and the main pump.
  • the backing pump pinion and the main pump pinion are arranged coaxially to one another and also the backing pump ring gear and the main pump ring gear.
  • the backing pump pinion axis and the Main pump pinion rotation axis together.
  • the backing pump ring gear axis and the main pump ring gear axis can be provided.
  • the fore pump pinion and the main pump pinion have identical dimensions in the radial direction.
  • the backing pump pinion and the main pump pinion are particularly preferably of identical or identical design.
  • the backing pump ring gear and the main pump ring gear additionally or alternatively have identical dimensions in the radial direction. They are particularly preferably constructed identically or identically.
  • the dimensions of the pinion are the dimensions of their outer circumference and the dimensions of the hollow wheels are the dimensions of their inner circumference.
  • the dimensions of the pinions and the ring gears correspond to the respective tip diameter of the corresponding teeth, that is, the external teeth of the pinion and the internal gears of the hollow wheels.
  • teeth of the backing pinion and the main pump pinion and / or teeth of the backing ring gear and the main pump ring gear are arranged offset in the circumferential direction from one another, for example by half a tooth spacing. In this way, pulsations in the fluid delivery device can be avoided.
  • the backing pump has a higher limit speed than the main pump, and / or that the backing pump has a larger pump volume than the main pump. Due to the at least partially or completely missing compensation of the backing pump, it is suitable for higher limiting speeds than the compensated main pump.
  • the fluid delivery device ensures that the main pump is always optimally supplied with fluid by the backing pump.
  • the backing pump has the larger pump volume compared to the main pump.
  • the pump volume can also be referred to as the geometric delivery volume. This in turn describes a delivery volume of the respective pump during one revolution of the respective input shaft, that is to say the backing pump input shaft for the backing pump and the main pump input shaft for the main pump.
  • the geometric delivery volume neglects tolerances, play and deformations that can occur during operation of the respective pump.
  • the larger pump volume of the backing pump enables the main pump to be reliably supplied with the fluid over the long term.
  • the backing pump and the main pump are arranged in a common machine housing.
  • the machine housing is designed in such a way that the fore pump pinion and the fore pump hollow wheel, seen in the axial direction from one side, and the main pump pinion and the main pump ring gear are introduced into the machine housing from the other side during assembly of the fluid delivery device.
  • a partition is arranged in the machine housing, which separates the backing pump and the main pump from one another at least in certain areas.
  • the backing pump and the main pump are preferably adjacent in the axial direction, in particular spaced from one another, that is to say seen in the axial direction without overlap, in the machine housing.
  • a suction chamber of the backing pump configured as an internal gear pump extends over a larger angular range than a suction chamber of the main pump, and / or that a pressure chamber of the backing pump extends over at least the same angular range as a pressure chamber of the main pump.
  • the suction chamber and the pressure chamber are seen in cross section in the radial direction between the pinion and the ring gear of the respective pump.
  • the suction chamber and the pressure chamber are each limited in the radial direction inwards by the pinion and in the radial direction outwards by the ring gear.
  • the pinion and the ring gear of the respective pump are designed such that they require fluid in the suction chamber in the direction of the pressure chamber.
  • the fluid is supplied to the suction chamber in the axial direction and / or in the radial direction.
  • at least one inlet channel is formed in the machine housing.
  • the respective ring gear has at least one recess that opens at least temporarily into the suction chamber.
  • the fluid can be removed from the pressure chamber in the axial direction and / or in the radial direction.
  • An outlet duct is formed in the machine housing for removal in the axial direction.
  • the ring gear has the recess, which is at least temporarily in flow connection with the pressure chamber. To this extent, a flow connection between the pressure chamber and the outlet channel or an outlet of the fluid conveying device is at least temporarily established via the recess.
  • the suction chamber of the backing pump extends over the larger angle range than the suction chamber of the main pump. This is particularly supported by a achieved different design of the filler, which is smaller for the backing pump in the circumferential direction than for the main pump. Due to the greater extent of the suction chamber of the pre-pump, a high speed of the backing pump is possible because the greater distance which is available for filling the suction chamber with fluid reduces the tendency of the backing pump to cavitate.
  • the larger dimensions of the suction chamber reduce the flow velocity of the fluid required to fill the suction chamber. Particularly preferred is the angular range over which the suction chamber of the backing pump extends by at least 25%, at least 50%, at least 75% or at least 100% larger than the angular range over which the suction chamber of the main pump extends.
  • the pressure chamber of the backing pump is at least as large in cross-section as the pressure chamber of the main pump, ie it extends over at least the same angular range.
  • the pressure chamber of the backing pump extends over a larger angular range than the pressure chamber of the main pump.
  • the angular range over which the pressure chamber of the backing pump extends is preferably greater by at least 10%, at least 20% or at least 25% than the angular range over which the pressure chamber of the main pump extends. This enables the high speed of the backing pump described above.
  • a further embodiment of the invention provides that the suction chamber and the pressure chamber of the backing pump are connected to one another in terms of flow directly via an overflow valve.
  • the overflow valve is designed such that when a certain pressure difference between the pressure chamber and the suction chamber is exceeded, it establishes a flow connection between the pressure chamber and the suction chamber and otherwise interrupts it.
  • the overflow valve serves as a pressure relief valve, which opens upon reaching or exceeding a certain pressure difference between the pressure chamber and the suction chamber, so that the pressure present in the pressure chamber can be reduced in the direction of the suction chamber.
  • the overflow valve closes as soon as the pressure difference between the pressure chamber and the suction chamber falls below the certain pressure difference again.
  • the overflow valve can be integrated in the machine housing or can be arranged outside the machine housing.
  • the overflow valve prevents the maximum pressure from being exceeded and / or the occurrence of cavitation in the backing pump, so that a reliable supply of the main pump with the fluid is always ensured.
  • the angular range over which the suction chamber of the backing pump configured as an internal gear pump extends in the circumferential direction is at least 180 °, at least 190 °, at least 200 °, at least 210 °, at least 220 ° or at least Is 225 °. With such an extension of the suction chamber in the circumferential direction, a reliable filling of the suction chamber is achieved even at high speeds of the backing pump.
  • a further development of the invention provides that in the backing pump configured as an internal gear pump, a backing pump filler between the backing pump pinion and the backing pump hollow wheel and in the main pump a main pump filling head is arranged between the main pump pinion and the backing pump main gear, wherein the backing pump filler is less in the circumferential direction with respect to an axis of rotation of the backing pump pinion Angular extent as the main pump filler in the circumferential direction with respect to an axis of rotation of the main pump pinion.
  • the respective filling piece serves to separate the pressure chamber from the suction chamber in terms of flow.
  • the filler piece lies in the radial direction or in cross-section, sealingly on the one hand on the respective pinion and on the other hand on the respective ring gear.
  • the fore pump filler is designed with a smaller angular extent in the circumferential direction than the main pump filler.
  • the angular extent of the respective filler is to be understood as the angle with respect to the respective pinion rotation axis.
  • a preferred further embodiment of the invention provides that the backing pump filling piece, the backing pump pinion and the backing pump ring gear are arranged and / or designed such that a sealing effect between the backing pump filler piece and the backing pump pinion and / or a sealing action between the backing pump filler head and the backing pump ring gear on one of the pressure chambers facing side of the backing pump filler is larger than on a side of the backing pump filler facing the suction chamber.
  • the cross-section of the backing pump filler lies, on the one hand, in a sealing manner on the backing pump pinion and on the other hand on the backing pump.
  • the sealing effect between the pre-pump filler and the pre-pump pinion on the side facing the pressure chamber is greater than on the side facing the suction chamber.
  • the sealing effect is greater, the greater the contact pressure of the backing pump filler against the backing pump pinion or the backing pump internal gear.
  • the pre-pump pinion is oversized with respect to the pre-pump filler and / or the pre-pump ring gear is undersized with respect to the pre-pump filler before commissioning, so that infeed wear occurs during running-in, as a result of which a play-free fit occurs is achieved.
  • the backing pump pinion or the backing pump ring are press-fit with respect to the backing pump filler, or vice versa, the backing pump filler with respect to the backing pump pinion and / or the backing pump ring gear.
  • the run-in wear occurs, through which the backing pump pinion, the backing pump ring gear and / or the backing pump filler are removed in such a way that there is subsequently a backlash-free fit, which realizes a particularly high sealing effect.
  • the backing pump filler piece particularly preferably consists of a softer material than the backing pump pinion and the backing pump internal gear, so that essentially the backing pump filler head is removed when it runs in. Due to the backlash-free fit that exists after running in, a particularly good seal between the pressure chamber and the suction chamber of the backing pump is achieved, which in turn leads to high pressures that can be achieved.
  • the centrifugal pump has an impeller, wherein a diameter of the impeller has at most 125% of an outer diameter of the main pump ring gear.
  • the impeller is intended to convey the fluid and is formed. At its largest point in the radial direction, it has the diameter. This should not more than 125% of the outer diameter of the main pump ring gear.
  • the outer diameter describes the outer diameter of the main pump wheel at its largest point in the radial direction. It is preferably provided that the diameter of the impeller corresponds to the outer diameter of the main pump ring gear, as being the same size. However, it can also be provided that the diameter of the impeller is at most 90%, at most 80% or at most 75% of the outer diameter of the main pump ring gear or is generally smaller. In this way, a compact design of the Fluid livingeinrich device is achieved.
  • the impeller of the centrifugal pump is arranged coaxially with the skin pump pinion.
  • the impeller of the centrifugal pump can be driven via the backing pump input shaft, in particular it is rigid and / or permanently connected to it, for example it is formed in one piece with the backing pump input shaft.
  • the Vorpumpenein input shaft, to which the impeller of the centrifugal pump is coaxial and the main pump input shaft, to which the main pump pinion is coaxial can be designed in one piece and / or in a materially uniform manner.
  • the impeller of the centrifugal pump and the main pump pinion are preferably seated on the same shaft, namely the drive shaft of the fluid delivery device.
  • This enables a particularly advantageous coupling of backing pump and main pump.
  • the diameter of the impeller of the centrifugal pump and / or a number of blades of the impeller, a pressure that can be achieved by means of the centrifugal pump and / or a fluid flow rate that can be achieved by means of the centrifugal pump are selected such that cavitation-free operation of the main pump is ensured ,
  • the impeller of the centrifugal pump is preferably designed accordingly.
  • Ligur 1 is a schematic longitudinal sectional view through a fluid delivery device with a
  • FIG. 2 shows a schematic cross-sectional illustration through the fluid delivery device
  • Figure 3 is a schematic cross-sectional view through the fluid delivery device in the area of the backing pump
  • Figure 4 is a schematic longitudinal sectional view through the fluid delivery device in a further embodiment.
  • the fluid delivery device 1 shows a schematic longitudinal sectional view through a fluid delivery device 1, which has a backing pump 2 and a main pump 3 connected in terms of flow technology to the backing pump 2.
  • the fluid delivery device 1 has a fluid inlet 4 and a fluid outlet 5 and is designed such that it delivers fluid from the fluid inlet 4 in the direction of the fluid outlet 5.
  • the backing pump 2 is connected to the fluid inlet 4 directly, but only indirectly via the main pump 3 to the fluid outlet 5.
  • the main pump 3 is connected only indirectly via the backing pump 2 to the fluid inlet 4, but directly to the fluid outlet 5. This means that the fluid provided at the fluid inlet 4 is conveyed by the backing pump 2 in the direction of the main pump 3 and is further conveyed by the main pump 3 in the direction of the fluid outlet 5, at which it is subsequently available.
  • the backing pump 2 and the main pump 3 are arranged in a common machine housing 6 or pump housing, on which both the fluid inlet 4 and the fluid outlet 5 are formed.
  • a drive shaft 7 is rotatably gela, by means of which a backing pump input shaft 8 and a main pump input shaft 9 can be driven.
  • the Vorpumpeneingangswel le 8 and the main pump input shaft 9 are made in one piece and / or of the same material.
  • the drive shaft 7 is preferably non-rotatably coupled to the backing pump input shaft 8 and the main pump input shaft 9 via a positive connection, for example a tooth connection.
  • the backing pump 2 has a backing pump pinion 10 and a backing pump ring gear 11 and is designed as an internal gear pump.
  • the backing pump pinion 10 has an external toothing 12 which meshes in regions with an inside toothing 13 of the backing pump ring gear 11 for conveying the fluid.
  • the pump pinion 10 is connected in a rotationally fixed manner via a toothing to the fore-pump input shaft 8, but is displaceably connected in the axial direction.
  • the pre-pump pinion 10 is formed in one piece and / or with the same material as the pre-pump input shaft 8.
  • the backing pump 2 can be in the form of an external gear pump or a centrifugal pump.
  • the main pump 3 has a main pump pinion 14 and a main pump ring gear 15.
  • the main pump pinion 14 has an external toothing 16 which, viewed in the circumferential direction, meshes only in regions with an internal toothing 17 of the main pump ring gear 15.
  • a suction chamber 18 in the radial direction between the backing pump pinion 10 and the backing pump internal gear 11. This also applies to a pressure chamber 19.
  • the suction chamber 18 is directly connected to the fluid inlet 4 in terms of flow technology, the backing pump 2 being designed such that the fluid can flow into the suction chamber 18 on both sides, viewed in the axial direction. Accordingly, there is a flow connection from the fluid inlet 4 to both sides of the suction chamber 18.
  • the pressure chamber 19 is fluidically connected to the main pump 3 via a flow channel 20 formed in the machine housing 6, namely to a suction chamber 21 of the main pump, which is present in the radial direction between the main pump pinion 14 and the main pump ring gear 15.
  • the main pump 3 is designed in such a way that the flow channel 20, seen in the axial direction, is connected on both sides to the suction chamber 21 in terms of flow technology, so that fluid from the flow channel 20, seen in the axial direction, can flow into the suction chamber 21 of the main pump 3 on both sides.
  • recesses 22 are formed in the main pump ring gear 15, via which there is an additional flow connection between the flow channel 20 and the suction chamber 21.
  • the main pump 3 also has a pressure chamber 23 which is present in the radial direction between the main pump pinion and the main pump ring gear 15.
  • the pressure chamber 23 is in flow connection with the fluid outlet 5 via the recesses 22, preferably exclusively. This means that fluid present in the pressure chamber 23 can only escape from the pressure chamber 23 in the direction of the fluid outlet 5 via at least one of the recesses 22.
  • the main pump 3 is at least axially compensated in the exemplary embodiment shown here, that is to say has an axial compensation 24.
  • both sides of the main pump pinion 14 and the main pump ring gear 15 each have an axial disk 25 which is urged during operation of the main pump 3 in the direction of the main pump pinion 14 and the main pump ring gear 15 and on the end faces of the main pump pinion 14 and the main pump ring gear 15 fit tightly.
  • the axial disks 25 are pressurized from the pressure chamber 23 of the main pump 3.
  • an opening 26 is formed in the axial disks 25, via which the Pressure chamber 23 is in flow connection with a pressure field 27, which is present on the side of the axial disk facing away from the pressure chamber 23.
  • FIG. 2 shows a schematic cross-sectional illustration of the fluid delivery device 1, the backing pump pinion 10, the backing pump ring gear 11, the main pump pinion 14 and the main pump ring gear 15 being shown.
  • the backing pump pinion 10 is rotatably mounted about a backing pump pinion rotation axis 28, the backing pump ring gear 11 about a backing pump ring gear axis of rotation 29, the main pumping pinion 14 about a main pumping pinion rotation axis 30 and the main pumping ring gear 15 about a main pumping ring gear axis of rotation 31.
  • the backing pump pinion axis 28 and the backing pinion axis 28 are identical, so that the Vorpum penritzel 10 and the main pump pinion 14 are arranged coaxially to each other.
  • the Vorpum penhohlradwindachse 29 is spaced parallel to the Vorpumpenritzelmosachse 28 and the main pump ring gear axis of rotation 31 parallel to the main pump pinion rotation axis 30th
  • the main pumps ring gear rotation axis 31 and the backing pump ring gear rotation axis 29 are arranged on opposite sides of the backing pump pinion rotation axis 28.
  • the fore pump pinion rotation axis 28, the fore pump ring gear rotation axis 29, the main pump pinion rotation axis 30 and the main pump ring gear rotation axis 31 lie on an imaginary straight line, the fore pump ring gear rotation axis 29 and the main pump ring gear rotation axis 31 being arranged on opposite sides of the fore pump pinion rotation axis 28 and particularly preferably at the same distance exhibit.
  • teeth of the backing pinion 10 and teeth of the main pump pinion 14 are arranged offset to one another in the circumferential direction, that is, seen in the axial direction are not in overlap with one another or are not aligned with one another. This can effectively prevent the occurrence of pulsations.
  • an offset of half a tooth spacing is provided, so that each tooth of the backing pinion 10 is in the middle between two teeth of the main pump pinion 14 or vice versa.
  • any other offset in the circumferential direction can also be selected.
  • FIG. 3 shows a schematic cross-sectional illustration of the fluid delivery device 1 in the region of the backing pump 2.
  • the backing pump input shaft 8, the backing pump 10 and the backing ring gear 11, which are arranged in the machine housing 6, can be seen.
  • the angular range a, over which the suction chamber 18 extends in the circumferential direction is very large for both arrangements of the backing pump filler 32 and is at least 150 °, preferably at least 180 ° or more than 180 °. This ensures a particularly rapid filling of the suction chamber 18 with fluid.
  • the backing pump 2 is designed to be uncompensated and, in the exemplary embodiment shown here, has neither axial compensation nor radial compensation.
  • the main pump on the other hand, is designed to be compensated and, in the exemplary embodiment shown here, has at least axial compensation 24. Additionally or alternatively, the main pump 3 can be designed with radial compensation.
  • the described configuration of the fluid delivery device 1 enables a particularly high speed, in particular the backing pump 2. This ensures a reliable supply of the main pump 3 with fluid, so that overall the fluid delivery device 1 has a high delivery pressure or a large pressure ratio between the pressure at the Fluid outlet 5 and the pressure at the fluid inlet 4 realized.
  • FIG. 4 shows a schematic sectional view of the fluid delivery device 1 in a further embodiment.
  • the backing pump 2 is not designed as an internal gear pump, but as a centrifugal pump.
  • the backing pump 2 designed as a centrifugal pump has a fan wheel 33, which is present in the exemplary embodiment shown here as a radial pump running thread. Accordingly, the centrifugal pump is designed as a radial pump.
  • the fan wheel 33 has a diameter Di, which in the embodiment illustrated here represents an outer diameter D 2 of the main pump ring gear 15.
  • the diameter Di of the impeller 33 corresponds to at most 125% of the outer diameter D 2 of the main pump ring gear 15. It can be seen that the impeller 33 of the backing pump 2 is in turn arranged coaxially with the main pump pinion 14. This results in a particularly compact configuration of the fluid delivery device 1.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne un dispositif de refoulement de fluide (1) comprenant une pompe primaire (2) et une pompe principale (3) raccordée fluidiquement à la pompe primaire (2). La pompe primaire (2) peut être entraînée par l'intermédiaire d'un arbre d'entrée de pompe primaire (8), la pompe principale (3) peut être entraînée par l'intermédiaire d'un arbre d'entrée de pompe principale (9), et l'arbre d'entrée de pompe primaire (8) et l'arbre d'entrée de pompe principale (9) sont accouplés mécaniquement à un arbre d'entraînement commun (7) du dispositif de refoulement de fluide (1). Selon l'invention, la pompe primaire (2) est réalisée sous la forme d'une pompe à engrenage non compensée ou d'une pompe centrifuge et la pompe principale (3) est réalisée sous la forme d'une pompe à engrenage intérieur compensée.
EP19744680.0A 2018-07-26 2019-07-23 Dispositif de refoulement de fluide Pending EP3827170A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018212497.3A DE102018212497A1 (de) 2018-07-26 2018-07-26 Fluidfördereinrichtung
PCT/EP2019/069825 WO2020020902A1 (fr) 2018-07-26 2019-07-23 Dispositif de refoulement de fluide

Publications (1)

Publication Number Publication Date
EP3827170A1 true EP3827170A1 (fr) 2021-06-02

Family

ID=67439218

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19744680.0A Pending EP3827170A1 (fr) 2018-07-26 2019-07-23 Dispositif de refoulement de fluide

Country Status (5)

Country Link
US (1) US11624365B2 (fr)
EP (1) EP3827170A1 (fr)
CN (1) CN112513464B (fr)
DE (1) DE102018212497A1 (fr)
WO (1) WO2020020902A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR3128976B1 (fr) * 2021-11-08 2023-11-24 Thales Sa Pompe Hydraulique

Family Cites Families (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3532441A (en) * 1968-09-04 1970-10-06 Chandler Evans Inc Pumps with vapor handling element
JPS5893976A (ja) * 1981-11-30 1983-06-03 Kayaba Ind Co Ltd 二段内接ギヤポンプ
JPS5893977A (ja) * 1981-11-30 1983-06-03 Kayaba Ind Co Ltd 二段内接ギヤポンプ
JPH04111586U (ja) * 1991-03-12 1992-09-28 住友精密工業株式会社 多段ポンプ
JPH1047279A (ja) * 1996-04-22 1998-02-17 Nippon Oil Pump Kk ２段ポンプ装置
DE19647052C2 (de) * 1996-11-14 1999-06-10 Bosch Gmbh Robert Einrichtung zum Fördern von Arbeitsmedien einer Brennkraftmaschine eines Kraftfahrzeuges
US6179595B1 (en) * 1998-05-27 2001-01-30 Luk Getriebe-Systeme Gmbh Hydraulic gear machine having a transmission shaft in a bearing tube
DE19950206A1 (de) * 1999-10-19 2001-04-26 Bayerische Motoren Werke Ag Vorrichtung mit antriebskombinierten Umlaufverdrängerpumpen, insbesondere außenverzahnte Zahnradpumpen, vor allem für Brennkraftmaschinen
DE10159147A1 (de) * 2001-12-01 2003-06-18 Zahnradfabrik Friedrichshafen Hydraulische Zahnradpumpe
DE10352029A1 (de) * 2003-11-07 2005-06-16 SCHWäBISCHE HüTTENWERKE GMBH Verdrängerpumpe mit Vorladeeinrichtung
DE102005004657A1 (de) * 2005-02-02 2006-08-03 Eckerle Industrie-Elektronik Gmbh Innenzahnradmaschine
DE102007032103B4 (de) * 2007-05-16 2022-02-24 Robert Bosch Gmbh Pumpeneinheit mit einer Hauptpumpe und einer in ihrem Fördervolumen verstellbaren Ladepumpe
DE102007054808A1 (de) * 2007-11-16 2009-05-20 Robert Bosch Gmbh Pumpenbaugruppe zur synchronen Druckbeaufschlagung von zwei Fluidkreisen
WO2009146448A2 (fr) 2008-05-30 2009-12-03 Metaldyne Company Llc Système de pompe à fluide à sortie variable
DE102009045227A1 (de) * 2009-10-01 2011-04-21 Robert Bosch Gmbh Innenzahnradpumpe für eine hydraulische Fahrzeugbremsanlage
DE102010063313A1 (de) * 2010-12-17 2012-06-21 Robert Bosch Gmbh Axialscheibe für eine Zahnradpumpe und Zahnradpumpe mit einer solchen Axialscheibe
JP5987331B2 (ja) * 2012-02-02 2016-09-07 株式会社ジェイテクト 電動オイルポンプ装置
JP5893977B2 (ja) 2012-03-22 2016-03-23 京セラ株式会社 液体吐出ヘッドおよびそれを用いた記録装置
DE102012217484A1 (de) 2012-09-26 2014-03-27 Robert Bosch Gmbh Innenzahnradpumpe, insbesondere für eine hydraulische Fahrzeugbremsanlage
DE202013103826U1 (de) 2013-05-13 2013-09-09 Eckerle Industrie-Elektronik Gmbh Innenzahnradmaschine mit Füllstück-Rückhalteeinrichtung
DE102013211615A1 (de) 2013-06-20 2014-12-24 Robert Bosch Gmbh Innenzahnradpumpe
JP6193068B2 (ja) * 2013-09-20 2017-09-06 住友精密工業株式会社 両回転型二連内接ギヤポンプ
CN104806468A (zh) * 2015-04-15 2015-07-29 北京航科发动机控制系统科技有限公司 一种同轴一体化高低压泵及加工方法

Also Published As

Publication number Publication date
US11624365B2 (en) 2023-04-11
CN112513464B (zh) 2023-05-26
US20210285448A1 (en) 2021-09-16
DE102018212497A1 (de) 2020-01-30
WO2020020902A1 (fr) 2020-01-30
CN112513464A (zh) 2021-03-16

Similar Documents

Publication Publication Date Title
EP1828611B1 (fr) Pompe a palettes coulissantes
EP3236074B1 (fr) Pompe rotative comprenant une rainure de graissage dans une nervure d'étanchéité
WO2000039465A1 (fr) Ensemble de pompes comportant deux pompes hydrauliques
EP1828609B1 (fr) Pompe rotative a ailettes
WO2009092719A2 (fr) Pompe à engrenage intérieur, à volume variable
DE19952167A1 (de) Pumpenanordnung mit zwei Hydropumpen
EP1934479A1 (fr) Pompe a palettes
EP3827170A1 (fr) Dispositif de refoulement de fluide
DE102008054474B4 (de) Innenzahnradpumpe mit optimiertem Geräuschverhalten
EP2655801B1 (fr) Machine à piston rotatif remplissant la fonction d'une pompe, d'un compresseur ou d'un moteur
DE102016207093B4 (de) Zahnradfluidmaschine
EP3032105B1 (fr) Pompe à vide mécanique pour véhicule automobile
DE102018204086B4 (de) Zahnradfluidmaschine
WO2012045837A2 (fr) Transmission hydraulique
EP3728850B1 (fr) Dispositif de transport de fluide
WO2004046554A1 (fr) Pompe a roue a denture interieure
DE102006036439A1 (de) Förderaggregat
DE102012217484A1 (de) Innenzahnradpumpe, insbesondere für eine hydraulische Fahrzeugbremsanlage
WO2009019101A1 (fr) Pompe refoulante
WO2016180570A1 (fr) Pompe volumétrique, procédé de fonctionnement d'une pompe volumétrique, système de direction et mécanisme
DE19713907A1 (de) Verdrängermaschine
WO2014121862A1 (fr) Pompe volumétrique à volume de refoulement variable
WO2022058350A1 (fr) Moteur de type gérotor à deux étages
DE102010064193A1 (de) Innenzahnradpumpe
EP4198309A1 (fr) Pompe à vis

Legal Events

Date Code Title Description
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: UNKNOWN

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE INTERNATIONAL PUBLICATION HAS BEEN MADE

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

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: 20210226

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

DAV Request for validation of the european patent (deleted)
DAX Request for extension of the european patent (deleted)
STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: EXAMINATION IS IN PROGRESS

17Q First examination report despatched

Effective date: 20230203