EP3263835B1 - Flügelzellenpumpe mit druckbeaufschlagbarem unterflügelbereich - Google Patents

Flügelzellenpumpe mit druckbeaufschlagbarem unterflügelbereich Download PDF

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Publication number
EP3263835B1
EP3263835B1 EP17177916.8A EP17177916A EP3263835B1 EP 3263835 B1 EP3263835 B1 EP 3263835B1 EP 17177916 A EP17177916 A EP 17177916A EP 3263835 B1 EP3263835 B1 EP 3263835B1
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EP
European Patent Office
Prior art keywords
flow
flow path
resistance
passage
outlet
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
EP17177916.8A
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German (de)
English (en)
French (fr)
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EP3263835A1 (de
Inventor
Claus Welte
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.)
Schwaebische Huettenwerke Automotive GmbH
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Schwaebische Huettenwerke Automotive GmbH
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Publication of EP3263835A1 publication Critical patent/EP3263835A1/de
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0854—Vane tracking; control therefor by fluid means
    • F01C21/0863—Vane tracking; control therefor by fluid means the fluid being the working fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F01C21/108—Stators; Members defining the outer boundaries of the working chamber with an axial surface, e.g. side plates
    • 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
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3446—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member the inner and outer member being in contact along more than one line or surface
    • 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
    • F04C2210/00—Fluid
    • F04C2210/20—Fluid liquid, i.e. incompressible
    • F04C2210/206—Oil

Definitions

  • the invention relates to a vane pump with at least one vane and an associated lower vane area, into which a pressure fluid to be pumped can be introduced in order to pressurize the vane.
  • vane pumps of the type mentioned the vane or the several vanes are acted upon in each case in the lower vane area with the pressure fluid conveyed by the pump, in order to ensure that the vane (s) is also directed outwards in the lower speed range, such as when the pump starts up are pressed onto a curve structure surrounding the rotor in order to fluidly separate the pumping cells of the pump from one another.
  • the supply to the lower wing area is accompanied by a reduction in pump efficiency.
  • the DE 10 2013 113 894 A1 shows a vane pump, the lower vane area is supplied with pressurized fluid through supply passages, so that the vanes are pressed radially outward against a curved structure.
  • the pump provides a resilient cover element.
  • the cover element is designed in such a way that it axially covers both the pressure passages from which the pressure fluid flows out of the delivery cells and the supply passages which ensure the supply of the lower wing areas with pressure fluid.
  • a disadvantage of such a design of the cover element is that the pressure fluid flowing out of the delivery chamber entirely flows against the cover element and is thereby deflected. In addition to pressure losses due to wall friction, the deflection of the flow has the effect that an additional swirl is forced on the flow, which can lead to backflows and to an increase in the back pressure of the pump.
  • the invention relates to a vane pump with a rotor that can be rotated about an axis of rotation and one or more vanes that can be moved back and forth in an associated, preferably slot-shaped, vane mount of the rotor.
  • the word "a” is understood only in the phrase “one or more” as a numerical word, otherwise always as an indefinite article.
  • a curve structure surrounds the rotor and delimits a pump delivery chamber radially on the outside. The rotor limits the delivery space radially on the inside. When the rotor rotates, the curve structure guides the wing or vanes, so that during the rotation, periodically increasing and decreasing conveyor cells are formed.
  • the curve structure has a guide curve on an inside radially facing the rotor, against which only one wing or, preferably, a plurality of wings press, so that a sealing gap is formed between the curve structure and the respective wing, which gap adjoins the respective wing. fluidly separates adjacent feed cells.
  • the curve structure can be magnetic to attract the wing or wings to the outside.
  • the vane pump further includes an end plate axially facing the rotor with a pressure passage for removing pressure fluid from the pump and a supply passage for supplying a lower vane region with pressure fluid that is branched from the pressure fluid that flows through the pressure passage. If the vane pump has a plurality of vanes which can be moved back and forth in vane receptacles of the rotor, a lower vane region is formed in each of the vane receptacles and is supplied with the pressurized fluid via the one or the supply passages of the end plate during pump operation.
  • the end plate delimits the delivery space on one end of the rotor.
  • a housing part delimits the delivery space on the other end of the rotor.
  • the end plate can be firmly assembled from several separately manufactured pieces, but it is preferably formed in one piece as a whole by a process of original shaping.
  • the term "end plate” should not be understood to mean that the end plate must be a plate in the narrow sense.
  • facing the rotor it can have a flat end face with which it delimits the delivery space on the relevant end face of the rotor.
  • the face plate can have one or more pressure passages and / or one or more supply passages.
  • the pump can be single-flow or multi-flow. In the case of a single-flow pump, it can also have a plurality of pressure passages on the high-pressure side, which are provided in expedient designs in the end plate. If the pump is a multi-flow pump, the end plate expediently has at least one pressure passage per flood. Regardless of the question of whether the pump is single-flow or multi-flow, the face plate can have one or more supply passages. It preferably has at least one supply passage per flood. If there are several supply passages, each of the supply passages can be provided in the end plate. Insofar as features of the printing pass are described, each additional printing pass preferably also has these features in the presence of several printing passes. Insofar as features of the supply passage are described, each additional supply passage preferably also has these features in the presence of several supply passages.
  • the pressure fluid flowing through the pressure passage is conveyed by means of a flow guide device on an end face of the end plate axially facing away from the rotor on different flow paths through a first outlet area and a second outlet area of the pump.
  • the first outlet area serves to discharge a first partial flow of the pressure fluid flowing through the pressure passage.
  • the second outlet area serves to discharge a second partial flow of the pressure fluid flowing through the pressure passage.
  • the first outlet area and / or the second outlet area can be formed in one advantageous embodiment as one or more through openings of the flow guide device.
  • the flow guide device can be part of the end plate. It can be firmly joined to the end plate, for example welded, glued or screwed. It can also be formed together with the face plate in a process of original shaping. In preferred embodiments, however, the flow guide device is manufactured separately from the end plate and is assembled, preferably detachably, when the pump is assembled. When assembled, it is preferably in direct contact with the end plate. In the assembled state, it preferably has axial pressure contact with the end plate.
  • a flow guide area formed by means of the end plate and flow guide device on the high pressure side of the pump is designed such that a first flow path, a second flow path and at least one further, third flow path are formed for the pressure fluid flowing from the pressure passage of the end plate.
  • the first partial flow of the pressure fluid flows through the first outlet region on the first flow path.
  • the second flow path branches off from the first flow path and connects the Pressure passage with the supply passage of the face plate.
  • the flow guide device delimits the second flow path, preferably at least in the axial direction, so that the branched pressure fluid flows on the second flow path between the flow guide device and the facing end face of the end plate to the supply passage.
  • the third flow path connects the supply passage to the second outlet area, so that pressure fluid can flow from and through the supply passage to the second outlet area.
  • the third flow path is likewise delimited by the flow guide device, preferably at least in the axial direction, so that pressure fluid flows on the third flow path between the flow guide device and the facing end face of the end plate to the second outlet area.
  • the supply of the lower wing area can be ensured via the second flow path, but on the other hand the first partial flow on the first Flow path can be removed directly with a short distance and therefore with little loss of flow.
  • the first outlet area overlaps with a downstream outlet opening of the pressure passage in the axial view, so that the first partial flow from the downstream outlet opening of the pressure passage flows in the axial direction over a short distance to the first outlet area and preferably also flows axially through the first outlet area from the pump can.
  • the first outlet area overlaps only a first partial area of the downstream outlet opening of the pressure passage in the axial view
  • the flow guide device overlaps a second partial area of the downstream outlet opening of the pressure passage, so that only a part of the pressure fluid flowing through the pressure passage as the first partial flow through the flows out of the first outlet area and another part of the pressure fluid flowing through the pressure passage is directed from the flow guide device to the side into the second flow path.
  • the flow guide device can act as a baffle device deflecting the relevant part of the flow. Due to the division into the first partial flow flowing through the first outlet area and the further partial flow diverted into the second flow path, the first partial flow is removed axially in a short way and therefore with little loss, but on the other hand a flow in the direction of the supply passage and thus a reliable supply of the Lower wing area forced.
  • the flow resistance of the third flow path which leads from the supply passage to the second outlet area, is greater than the flow resistance of the second flow path, on which the branched pressure fluid from the point of the branch to Supply passage flows.
  • the flow resistance of the first flow path can be greater than the flow resistance of the second flow path.
  • a resistance structure can be arranged in the first flow path in order to increase the flow resistance of the first flow path.
  • a resistance structure can be arranged in the third flow path in order to increase the flow resistance of the third flow path.
  • a resistance structure is arranged both in the first flow path and in the third flow path in order to increase both the flow resistance of the first flow path and the flow resistance of the third flow path.
  • the increase in the flow resistance of both flow paths can be achieved by arranging separate resistance structures, a resistance structure for the first flow path and a further resistance structure for the third flow path. More preferably, however, when the resistance of both paths increases, the resistance structure in the first flow path and the resistance structure in the third flow path are formed by the same resistance structure.
  • the one or more resistance structures belongs to the flow control device.
  • the flow guide device can consist of a flow guide structure manufactured as a structural unit, which at the same time also forms the one or more resistance structures.
  • the flow guide device can also be in several parts and include a flow guide structure and one or more resistance structure (s) manufactured separately from it.
  • the flow guide device can in particular be in two parts and consist of a flow guide structure and a resistance structure.
  • the flow guide device comprises a flow guide structure, a resistance structure and a stop structure, it being possible in such embodiments to consist in particular of these three structures.
  • the resistance structure and the stop structure can advantageously form one or more valves in the first flow path and / or one or more valves in the second flow path, each in the form of a reed valve.
  • the resistance structure can in particular be an axially thin, flat structure.
  • the resistance structure can be, for example, a sheet metal structure or a sheet-like structure, the word "sheet metal” primarily describing only the shape of the resistance structure, but not intended to restrict the resistance structure with regard to the material.
  • sheet metal primarily describing only the shape of the resistance structure, but not intended to restrict the resistance structure with regard to the material.
  • preferred materials are metals and metal alloys, especially steels.
  • a thin, flat resistance structure is easy to assemble and can be designed simply and flexibly with regard to the flow conditions to be achieved.
  • the resistance structure is preferably arranged axially between the end plate and the flow guide structure.
  • One or more further structures, preferably each with a thin surface, can be arranged axially between the end plate and the resistance structure.
  • one or more structure each preferably thin in area, can be arranged, for example the abovementioned system structure.
  • the end plate, the resistance structure, the flow guiding structure and one or more optional further structures are preferably arranged in layers lying one against the other.
  • the resistance structure is axially preferably directly adjacent to the end plate.
  • the flow guide device can be in one piece in simple designs or in multiple pieces, in particular in two pieces, in alternative designs.
  • the flow guide device consists of a flow guide structure, in multi-part versions it includes a flow guide structure.
  • the flow guide structure delimits at least a part of the first outlet area and / or a part of the second outlet area.
  • the flow guide structure has one or more of one another separate passageways, which together form the first outlet area.
  • the flow guide structure can have one or more passages which are separate from one another and which together form the second outlet region.
  • the respective passage can lie completely within the flow guide structure, that is to say it can be surrounded on all sides by it.
  • the flow guide structure does not have to have a structural region that separates the outlet regions from one another.
  • the first outlet area and the second outlet area can directly adjoin one another. In embodiments of this type, it is advantageous if the flow guide structure forms the first and the second outlet region as a common outlet that is surrounded on all sides by the flow guide structure.
  • the flow guidance according to the invention in the flow guide area is obtained by correspondingly arranging the first outlet area and the second outlet area relative to the outlet opening of the pressure passage.
  • the first outlet region and the second outlet region can in particular be arranged relative to the outlet opening of the pressure passage in such a way that the first flow path is shorter than the sum of the lengths of the second flow path and the third flow path.
  • the first flow path is preferably also shorter than the third flow path and / or the second flow path, the flow paths being considered individually in relation to this relation.
  • an annular strip-shaped passage of the flow guide structure can advantageously form this common outlet.
  • the first outlet region and the second outlet region can be arranged directly next to one another in the circumferential direction of the annular strip-shaped passage.
  • the vane pump can in particular be installed in vehicles, preferably in motor vehicles, or be provided for such an installation.
  • the pump is preferably used as a hydraulic pump, the pressure fluid is a liquid in such applications.
  • the pump can be used, for example, as a lubricating oil pump for supplying a combustion drive engine of a motor vehicle or another unit of a motor vehicle with lubricating oil and / or cooling oil.
  • the pump can also serve as a working pump for supplying an assembly with a working fluid, preferably a working fluid such as hydraulic oil.
  • the use as a gear pump for supplying a gear, in particular an automatic transmission of a vehicle, with gear oil is a further preferred use.
  • the pump can also be used advantageously outside of vehicle technology, for example to supply a stationary internal combustion engine. It can also be used to supply an internal combustion engine Be used on board a watercraft or aircraft with lubricating oil or a working medium.
  • a gear pump for supplying a gear of a wind power plant or a gear of a plant for generating energy.
  • the vane pump can be designed as a so-called cartridge pump.
  • the vane pump according to the invention can be used as an assembled structural unit completely in a pot-shaped installation space and can be fixed in the installation space. Solutions of this type are known, for example, for gear pumps which are inserted in the pump installation space of a gear in the axial direction and are secured in the installation position, for example by means of a snap connection.
  • a cartridge pump of this type is, for example, from the DE 10 2015 105 928 A1 known.
  • the vane pump according to the invention can correspond to this known cartridge pump.
  • the vane pump according to the invention differs from the known pump with regard to the flow guide area designed by means of the flow guide device and the relevant features of the flow guide.
  • FIG. 1 shows a vane pump in a cross section.
  • the vane pump comprises a housing with a delivery chamber, in which a rotor 10 is arranged so as to be rotatable about an axis of rotation R.
  • a rotor 10 is arranged so as to be rotatable about an axis of rotation R.
  • Several blades 11 are arranged distributed over the circumference of the rotor 10.
  • the vanes 11 are guided in the slot-shaped vane receptacles of the rotor 10, which are open on the outer circumference of the rotor 10, so that they can move in the radial direction.
  • the wing receptacles extend radially, but could also be tilted to the radial direction or curved with a corresponding shape of the wings 11, so that the retracting and extending movement of the wings 11 or the optionally curved wings is a movement in the radial and / or tangential direction.
  • the pump is double-flow.
  • the delivery room is accordingly divided into two delivery chambers, each with an inlet and an outlet.
  • fluid flows through the inlet on the low-pressure side of the respective flood into the respective delivery chamber and is expelled and removed through the respective outlet while increasing the pressure on the high-pressure side of the respective flood.
  • the vanes 11 When the rotor 10 is driven in rotation, the vanes 11 are guided on the outside along a curve structure 5 surrounding the rotor 10 about the axis of rotation R, so that the vanes 11 move correspondingly deep into the vane receptacles of the rotor 10 according to the guide curve formed by the inner circumference of the curve structure 5. At a sufficiently high rotational speed, the vanes 11 are moved outwards by the centrifugal force, in the direction of the guide curve of the curve structure 5, so that 5 sealing gaps form between the vanes 11 and the curve structure 5, the feed cells adjoining the respective vanes 11 leading and trailing separate them fluidically.
  • the feed cells in the one feed chamber that increase on the low-pressure side and decrease on the high-pressure side are designated by 6 and the feed cells that increase on the low-pressure side and decrease on the high-pressure side by 7 when passing through the other feed chamber.
  • the wings 11 extend even at a low rotational speed, they are pressurized on their undersides near the axis of rotation R in a lower wing area 12 of the respective wing receptacle.
  • part of the pressure fluid conveyed by the pump is directed into the lower wing areas 12 in order to act on the undersides of the wings 11 and to apply a pressure force to the outside in the direction of the guide curve of the curve structure 5.
  • Figure 2 shows the vane pump in a longitudinal section.
  • the housing of the pump comprises a housing part 3, an end plate 4 and the curve structure 5.
  • the curve structure 5 is arranged axially between the housing part 3 and the end plate 4, so that the curve structure 5 surrounds the delivery chamber of the pump and the housing part 3 and the end plate 4 with their axially facing end faces, surround the delivery chamber axially on both outer sides of the rotor 10.
  • the curve structure 5 is part of the housing of the pump.
  • the curve structure 5 can be arranged to move back and forth in a modified pump housing in order to be able to adjust a specific delivery volume of the vane pump.
  • the curve structure 5 could be arranged to be linearly movable relative to the rotor 10.
  • an increase in the specific production volume of one flood would go hand in hand with a decrease in the specific production volume of the other flood.
  • This connection would not apply to single-flow pumps.
  • the curve structure 5 could, as is known in principle, be arranged to be linearly movable or pivotable relative to the rotor of a single-flow pump.
  • the pump can be designed with radially smaller dimensions and thus radially more compact than a pump with adjustable delivery volume.
  • the rotor 10 is connected in a torque-transmitting manner to a drive shaft 1 which is driven by a drive wheel 2.
  • the drive wheel 2 is accordingly connected to the drive shaft 1 in a torque-transmitting manner.
  • the drive shaft 1 extends through the housing part 3 and also the rotor 10 and projects with one axial end into the end plate 4, so that it is rotatably supported on both sides of the rotor 10 on the housing of the vane pump.
  • a first pressure passage 14 extends through the end plate 4, through which the pressure fluid on the high-pressure side can be removed from the delivery chamber formed by the delivery cells 6.
  • a further, second pressure passage 14 extends through the end plate 4 for delivery from the delivery chamber 7.
  • the pressure passages 14 extend axially straight through the end plate 4.
  • An axially straight pressure passage is advantageous in terms of a low-loss outflow. Basically, they can Pressure passages 14 or just one pressure passages 14 have a different course through the end plate 4, for example, extend obliquely to the axial direction.
  • an overflow channel 9 extends through the curve structure 5.
  • the overflow areas 8 are connected to the axially opposite pressure passage 14 via the overflow channels 9 which extend axially in the curve structure 5.
  • the vane pump has a flow guide device 20 on the end face of the end plate 4 facing away from the rotor 10, which guides the pressure fluid downstream of the delivery chamber in cooperation with the end plate 4 on the high pressure side of the pump and forms a flow guide area together with the end plate 4.
  • the pressure fluid is conducted on the high-pressure side by means of the end plate 4 and the flow guide device 20 into different flow paths and on the flow paths before it flows out through outlet areas of the pump predetermined by the flow guide device 20.
  • a first partial flow S1 of the pressure fluid flowing out of the pressure passage 14 flows out through a first outlet region 24 of the flow guide device 20.
  • the first flow path P1 extends from an outlet opening of the pressure passage 14 axially facing the flow guide device 20 to the first outlet area 24 of the flow guide device 20 assigned to this pressure passage 14.
  • the flow guide device 20 has a first outlet area 24 per flood in axial alignment with the pressure passage 14 of the respective one Flood or production chamber.
  • the flow guide device 20 is designed in such a way that only a part of the pressure fluid flowing out of the respective pressure passage 14 flows out through the assigned first outlet region 24 in a short way, namely on the respective flow path P1, and another part of the pressure fluid flowing out of the respective pressure passage 14 directly next to the the respective first outlet region 24 to the side, preferably as in the exemplary embodiment in the direction of the axis of rotation R, is directed into a second flow path P2 which extends at least substantially transversely to the axis of rotation R.
  • the flow path P2 extends between the end plate 4 and the flow guide device 20. It is delimited by these two structures in the axial direction in each case.
  • Figure 3 shows the vane pump in a further longitudinal section, which extends through lower vane regions 12 and to the first outlet regions 24 ( Figure 2 ) is offset in the circumferential direction.
  • a section of the second flow path P2 is shown for each of the two floods by means of a directional arrow, the directional arrows denoted by P2 not only representing the second flow path P2, but being extended beyond the respective second flow path P2 into the lower wing region 12.
  • a plurality of supply passages 15 extend through the end plate 4 in overlap with the lower wing areas 12.
  • a lower wing area connection 13 is provided, which serves to distribute the pressure fluid into the lower wing areas 12.
  • the second flow path P2 extends from the location of the junction from that from the respective pressure passage 14 ( Figure 2 ) flowing pressure fluid up to an inlet opening of the respective supply passage 15. If the end plate 4 has a plurality of supply passages 15, as in the exemplary embodiment, the second flow path P2 is the flow path that extends from the respective branch to an inlet opening of a supply passage 15. If, seen from a first outlet area 24, a plurality of supply passages 15 are arranged one behind the other, the second flow path P2 extends in each case to the closest supply passage 15.
  • the partial flow branched off by means of the flow guide device 20 is distributed in the flow guide area formed between the end plate 4 and the flow guide device 20 and flows out as a second partial flow S2 through a second outlet area 26 formed by the flow guide device 20. At least part of the pressure fluid ultimately flowing out as the second partial flow S2 also flows on the second flow path P2 into the lower wing regions 12 before this pressure fluid flows out as part of the second partial flow S2 through the second outlet region 26.
  • the flow guiding device 20 is formed by a one-piece flow guiding structure, which is also identified below with the reference symbol 20.
  • the flow guide device of the first exemplary embodiment or the flow guide structure 20 forming it is positioned relative to the end plate 4 and fixed in the positioned state, and is therefore immovable relative to the end plate 4 in the assembled state. In particular, as in the exemplary embodiment, it can rest on the end face of the end plate 4 facing away from the rotor 10.
  • Figure 4 shows the vane pump in an axial view of the end face of the end plate 4 facing away from the rotor 10.
  • the flow guide structure 20 is removed, so that the outlet opening of the respective pressure passage 14 and the inlet opening of the respective supply passage 15 are exposed.
  • 17 with positioning elements are referred to, which project axially on the end face of the end plate 4.
  • the positioning elements 17 serve to position the flow guide structure 20. They can in particular be pin-shaped or bolt-shaped.
  • the vane pump is in the same axial view as in Figure 4 , but shown with the positioned flow guide structure 20.
  • Positioning counter-elements 27, which are in positioning engagement with the positioning elements 17, are formed on the flow guide structure 20 for positioning.
  • the flow guide structure 20 lies axially against the end plate 4 and is secured against rotational movements about the axis of rotation R by the positioning engagement of the positioning elements 17 and positioning counter-elements 27.
  • the positioning engagement can be frictional in relation to the axial direction, so that the positioning elements 17 and positioning counter-elements 27 also form a captive device for the flow guide structure 20.
  • the flow guide structure 20 When assembling the pump, the flow guide structure 20 is rotated relative to the end plate 4 into the positioning engagement of the positioning elements 17 and positioning counter elements 27. During the relative rotation, the respective axially protruding positioning element 17 slides in the circumferential direction along a passer 28, which is formed on an inner circumference of the flow guide structure 20, until it engages with the positioning counter element 27 following the passer 28 in the circumferential direction.
  • the positioning counter elements 27 are accordingly formed on the inner circumference of the flow guide structure 20 as a radial depression.
  • the flow guide structure 20 expediently contacts the end plate 4 in the axial direction, that is to say the flow guide structure 20 is expediently placed axially on the end plate 4 and rotated in contact with the latter in the positioning engagement.
  • the flow guide structure 20 serves as a protection against loss for the axially stacked pump structure.
  • the positioning elements 17 are joined to the housing part 3 and project axially therefrom and through the curve structure 5 and the end plate 4, so that all the pump components from the housing part 3 to the flow guide structure 20 are held together by the clamping positioning engagement.
  • the second flow paths P2, on which the pressure fluid deflected by the flow guide structure 20 and thereby branched off, flows from the pressure passages 14 to the supply passages 15, and furthermore third flow paths P3 are represented by directional arrows.
  • the pressure fluid flows from the supply passages 15 to the second outlet areas 26 on the third flow paths P3.
  • pressure fluid also flows from the pressure passages 14 bypassing the supply passages 15 to the second outlet areas 26.
  • the directional arrows for the flow paths P2 and P3 show how, by means of the flow guide structure 20, a partial flow is branched off from the pressure fluid flowing from the pressure passages 14 and at least a part of this partial flow is conducted on the second flow paths P2 to the supply passages 15, and finally to the third Flow paths P3 and in the second partial flow S2 to flow through the second outlet regions 26.
  • the pressure fluid conveyed by the pump is directly in a first partial flow S1 through the first outlet area 24 of the respective flood and in a remaining second partial flow S2 after deflection or branching and ensuring the supply of the lower wing area 12 conveyed through the second outlet regions 26.
  • the pump has a first outlet area 24 per flood.
  • the second outlet areas 26 cannot be clearly assigned to either of the two floods. They can also be understood as a single second outlet area 26 for both floods.
  • a first outlet area 24 and a second outlet area 26 of a flood are to be referred to.
  • these outlet areas are mentioned in the majority. Otherwise, the statements relating to a first outlet area 24, a second outlet area 26, one apply Pressure passage 14 and a supply passage 15 in the same way for one or more further outlet areas 24 and 26 as well as pressure passages 14 and supply passages 14.
  • the first outlet regions 24 and second outlet regions 26 can be formed as a single axial passage or a plurality of separate axial passages of the flow guide structure 20. If a single-flow pump had only a single first outlet area 24 and a single second outlet area 26, these outlet areas 24 and 26 could also be formed as a single axial passage or as two separate axial passages of a correspondingly adapted flow guide structure. A plurality of first outlet regions 24 and a plurality of second outlet regions 26, which are separated from one another, could also be provided for one or more floods. The same applies to single-flow pumps.
  • the second outlet regions 24 directly adjoin the first outlet regions 24.
  • the outlet regions 24 and 26 can also be separated from one another by a structural region of the flow guide structure 20 extending between a first outlet region 24 and a second outlet region 26 the pressure fluid cannot flow through.
  • the first outlet areas 24 are in axial alignment with the outlet openings of the pressure passages 14, so that the first outlet area 24 of the one flood in axial view with the outlet opening of the pressure passage 14 of the same flood and the other first outlet area 24 with the outlet opening of the pressure passage 14 of the another flood overlaps.
  • the pressure passages 14 and first outlet areas 24 of the two floods lie diametrically opposite one another via the axis of rotation R, that is to say are offset from one another by approximately 180 ° in the circumferential direction. Due to the axial overlap, the pressure fluid flowing through the respective pressure passage 14 can flow out axially through the outlet opening of the pressure passage 14 and flow axially over a short distance to and through the assigned first outlet area 24.
  • the first outlet area 24 overlaps only a part of the axially opposite outlet opening of the associated pressure passage 14 in each of the floods. Therefore, only a part of the pressure fluid flowing through the respective pressure passage 14 flows through the axially opposite first outlet area 24. Another part flows against an axially opposite deflection region 25 of the flow guide structure 20 and is thereby turned sideways, transversely to the axis of rotation R and in the axial view in the direction of the inlet openings Supply passages 15 deflected.
  • the deflection area 25, with which the flow guide device or guide structure 20 overlaps the outlet opening of the respective pressure passage 14, is located in the axial plan view between the first outlet area 24 of the respective pump flow and an inlet opening of the supply passages 15.
  • the flow guide structure 20 overlaps one in each case
  • Another part of the pressure fluid flowing out of the pressure passages 14 flows through the flow guide area formed by the end plate 4 and the flow guide structure 20, in order to subsequently also flow out of the pump via the second outlet area or areas 26.
  • the flow guide structure 20 directs the pressure fluid delivered by the pump such that the first partial flow S1 is discharged in a short way, with little resistance, through the first outlet area 24 of the respective flood, while a second partial flow is deflected and via a second outlet area 26 or more second Outlet areas 26 is discharged as a second partial flow S2.
  • the flow guide structure 20 is designed in the axial view with respect to the position, shape and size of the respective first outlet area 24 in such a way that the deflection and, consequently, the division into the partial flows takes place in such a way that the lower wing area 12 with the pressurized fluid even at low pump speeds supplied and the wings 11 are pressurized on their undersides.
  • the flow guide structure 20 has a guide area 21 radially on the inside and a positioning area 22 on the radially outside.
  • the positioning area 22 is ring-shaped and surrounds the guide area 21.
  • annular strip-shaped passage which forms the first outlet areas 24 and the second outlet areas 26 lying between them in the circumferential direction. The sequence thus results in the circumferential direction: first outlet region 24 - second outlet region 26 - first outlet region 24 - second outlet region 26, the first outlet regions 26 and second outlet regions 25 each directly adjoining one another and also smoothly merging into one another in the boundary region.
  • the guide area 21 forms the deflecting area 25, radially on the inside adjacent to the respective first outlet area 24, at which the pressure fluid emerging from the assigned pressure passage 14 is deflected into one of the second flow paths P2 and thus towards the supply passages 15.
  • the flow guide structure 20 further comprises a plurality of connecting elements 23 which connect the guide area 21 to the positioning area 22 connect.
  • the connecting elements 23 each bridge the annular strip-shaped passage of the flow guide structure 20.
  • the connecting elements 23 are spaced apart from one another in the circumferential direction. They act as spring elements and are meandering to improve the spring effect.
  • the guide area 21 can deflect in the axial direction in the unloaded state relative to the positioning area 22. In the assembled state, the positioning region 22 bears axially on the end plate 4, while the guide region 21 is axially spaced from the end plate 4.
  • the guide area 21 springs axially in the direction of the end plate 4 when an axial compressive force acts on the guide area 21.
  • the flow guide structure 20 acts in this way as a spring device, in the exemplary embodiment it is designed as a plate spring with a spring direction parallel to the axis of rotation of the rotor 10.
  • the flow guide structure 20 is used for simple assembly of the vane pump designed as a cartridge pump in an installation space provided for the pump, for example in an installation space of a transmission to be supplied with the pressure fluid by the vane pump.
  • the vane pump is inserted axially comparable to a cartridge into the adapted installation space with the flow guide structure 20 ahead until the flow control structure 20 abuts a rear end wall of the installation space designed as a bag space.
  • the flow guide structure 20 springs in until the housing part 3 with one in the Figures 2 and 3rd Recognizable securing area 19 arrives behind an annular securing element which is arranged in a front area of the installation space in order to axially secure the pump in the installed state.
  • the sprung-in flow guide structure 20 presses the pump axially against the securing element, so that the pump is clamped axially in the secured state.
  • the securing element is usually provided at the installation site, but could instead also be part of the pump in reverse of the circumstances.
  • the securing element can be a slotted spring washer, for example.
  • the pump according to the invention can, for example, as from the DE 10 2015 105 928 A1 known to be arranged in a pump installation space or to be provided for such an arrangement.
  • the flow guide structure 20 has a central passage. In the installed state, the flow guide structure 20 presses with spring force against a rear end wall of the installation space, so that leakage fluid can possibly emerge from the flow guide area through the central passage.
  • the flow guide structure in the central area can be closed or have a significantly smaller central passage in order to reduce an outflow in this area and, consequently, to reduce it Prevent security of supply of the lower wing area 12 regardless of the installation situation.
  • a discharge channel for the pressure fluid can be provided in an end wall of the installation space, against which the flow guide structure 20 axially rests in the assembled state, and the flow guide structure 20 can have the central passage, which in these versions forms a third outlet area of the flow guide structure 20.
  • Pressure fluid flowing out through the third outlet region can advantageously be discharged separately from the rest of the pressure fluid, in order, for example, to supply the pressure fluid to specific locations or regions of a transmission or an engine gallery. This allows the flow paths to the consumption points to be optimized.
  • FIGS Figures 6 to 8 A vane pump with a flow control device of a second embodiment is shown.
  • Figure 6 shows the vane pump in a plan view of the flow guide structure 20, and the Figures 7 and 8 show the pump in longitudinal sections offset from one another in the circumferential direction.
  • the vane pump corresponds to that in FIGS Figures 1 to 5 Pump shown, so that essentially only the modified flow control device explained and with respect to the vane pump reference is made to the above statements and the same reference numerals are used for the corresponding pump components as there.
  • the flow guide device of the second exemplary embodiment comprises a flow guide structure 20 and additionally a resistance structure 30, which together form the flow guide device 20, 30 of the second exemplary embodiment.
  • the flow guide structure 20 corresponds to the flow guide structure 20 of the first exemplary embodiment, so that reference is also made in this regard to the above statements and the same reference numerals are used as there.
  • the flow resistance of the third flow path P3 is increased in relation to the flow resistance of the second flow path P2 in comparison to the first exemplary embodiment. This ensures with greater certainty that the lower wing area 12 ( Figures 1-3 ) is sufficiently supplied with pressurized fluid even at low speed.
  • the resistance structure 30 is in the flow path of the partial flow S2 flowing through the respective second outlet region 26 downstream of the respective supply passage 15, as preferably upstream, particularly preferably immediately before each outlet area 26 arranged.
  • the pressure fluid flowing through the respective second outlet region 26 flows through the resistance structure 30 in preferred embodiments directly upstream of the second outlet region 26 formed by the flow guide structure 20.
  • the flow resistance of the first flow path P1 can be increased in relation to the flow resistance of the second flow path P2 in comparison to the first exemplary embodiment.
  • this measure is implemented by the resistance structure 30 also increasing the flow resistance directly upstream of the first outlet region 24 of the respective flood.
  • the first partial flow S1 flows through the resistance structure 30 immediately before it flows out through the respective first outlet region 24.
  • the resistance structure 30 forms in the respective flow path P1 and / or P3, in the exemplary embodiment in the flow paths P1 and P3, an orifice with a plurality of passages 31, in the exemplary embodiment circular through holes through which the pressure fluid must flow, in order to then pass through the respective outlet area 24 or 26 to be able to flow off.
  • the flow resistance obtained by means of the resistance structure 30, which is additional in comparison to the first exemplary embodiment, depends on the ratio of the area of the passages 31 to the area of the closed, non-flowable areas of the resistance structure 30.
  • the flow resistance of the respective flow path P1 and / or P3 can therefore be varied in order to ensure the supply of the lower wing area 12 on the one hand, but to impair the efficiency of the pump as little as possible on the other hand.
  • the resistance structure 30 is an axially thin, flat structure. In the exemplary embodiment, it is a disk. It can be shaped flat as in the exemplary embodiment or instead in the form of a shell, for example following the shape of the flow guide structure 20.
  • the flow guide structure 20 and the resistance structure 30 are manufactured separately from one another. They can be assembled together or one after the other.
  • the resistance structure 30 is arranged between the end plate 4 and the flow guide structure 20. In particular, as in the exemplary embodiment, it can be arranged directly between the end plate 4 and the flow guide structure 20. It divides the flow guiding region formed between the end plate 4 and the flow guide structure 20 into one between the end plate 4 and the resistance structure 30 inner guide area and an outer guide area located between the resistance structure 30 and the flow guide structure 20.
  • the pressure fluid flowing out of the respective pressure passage 14 must flow through the resistance structure 30 in order to get into the outer guide region and to be able to flow out through the outlet regions 24 and 26.
  • FIGS Figures 9 to 11 show a vane pump with a flow control device of a third embodiment. Apart from the flow control device, the vane pump corresponds to that in FIGS Figures 1 to 5 Pump shown, so that reference is made to the explanations there and the reference numerals used there.
  • the flow guide device of the third embodiment is derived from the flow guide device of the second embodiment.
  • the flow guide structure 20 corresponds to the flow guide structure 20 of the two previous exemplary embodiments.
  • the flow guide device comprises a resistance structure 30 with a plurality of passages 31, which are each arranged in a surface area of the resistance structure 30 that is in axial overlap with the first outlet area 24 of the respective flood.
  • the resistance structure 30 corresponds to that of the second exemplary embodiment.
  • the resistance structure 30 has no passages in the region of the second outlet region 26 of the respective flood.
  • the top view of the resistance structure 30 has in each case a radially outwardly extended, closed resistance surface 32, which with the outlet region 26 of the respective flood in the top view, ie. H. axially, overlapped and the respective partial flow S2 must flow around before the respective partial flow S2 can flow out through the respective second outlet region 26.
  • a comparable resistance surface 32 could also be provided in the axial overlap with the respective first outlet region 24 instead of the passages 31 and enlarge the deflection region 25 of the first exemplary embodiment directly adjacent to the outlet region 24 and reduce the cross section of the outlet region 24 accordingly.
  • the resistance structure 30 in the axial overlap with the respective second outlet region 26 can have passages 31 as in the second exemplary embodiment and a closed resistance surface 32 in the axial overlap with the respective first outlet region 24.
  • the resistance structure 30 is designed in the manner of an aperture.
  • the modified resistance structure is formed, for example, as a sieve, fabric or other knitted fabric.
  • Several simple knitted fabric structures for example several simple sieves, can also form the modified resistance structure in an axially stacked manner.
  • the resistance structure can be composed of one or more non-flowable sub-areas and one or more flowable sub-areas, the flowable area or sub-areas being located in the first flow path P1 and / or the third flow path P3, by the flow resistance of the respective one Enlarge flow paths.
  • the one or more flowable areas can each be formed as an aperture or knitted fabric.
  • the Figures 12 to 14 show a vane pump with a flow control device of a fourth embodiment.
  • the vane pump corresponds to the vane pump of the above exemplary embodiments, so that reference is made to the explanations in this regard and the same reference numerals are used for the same pump components as in the first exemplary embodiment.
  • the flow guiding device of the fourth exemplary embodiment comprises a flow guiding structure 20 which corresponds to the flow guiding structure 20 of the above exemplary embodiments, so that reference is also made in this regard to the explanations given there.
  • the flow guide device forms a valve device with movable valve elements for controlling the discharge through both the first outlet area 24 and the second outlet area 26 of the respective pump flow.
  • the valve device comprises valves arranged distributed in the circumferential direction.
  • the flow guide device can have a valve for the first outlet region 24 of the respective flood and a plurality of valves for the second outlet region 26 of the respective flood.
  • the valves each comprise a movable valve element and a stop, namely a valve element 33 and a stop 41 for the first outlet area 24 of the respective flood and a plurality of valve elements 34 and associated stops 42 for the second outlet area 26 of the respective flood.
  • the movable valve elements 33 and 34 are between a closed position and a passage position predetermined by the respectively assigned stop 41 and 42 forth movable. When the pressure fluid is applied, the respective valve element moves axially outward in the direction of the passage position until it abuts the associated stop.
  • FIGs 13 and 14 the area of the vane pump comprising the flow guide device is shown in each case in a longitudinal section, as in the other exemplary embodiments.
  • the pressure passages 14 with the respectively assigned valve element 33 can be seen in longitudinal section.
  • Figure 14 shows in longitudinal section the supply passages 15 and the movable valve elements 34 arranged directly in front of the second outlet region 26
  • Figures 13 and 14 the valve elements 36 and 37 each take the closed position.
  • the valves are each designed in the manner of a reed valve.
  • the valve elements 33 and 34 are spring tongues, which each protrude from a root region in the circumferential direction and elastically from the end plate 4 in the direction of the respectively assigned stop, ie. H. are bendable in the direction of the passage position.
  • valve elements 33 and 34 are acted upon by the delivered pressure fluid in the direction of the open position.
  • the elastic restoring force of the valve elements 33 and 34 counteracts the pressure of the pressure fluid.
  • the elastic restoring force can in particular be dimensioned such that the valve elements 33 and / or 34 only move from the closed position towards the open position when a certain minimum speed is reached, so that the pressure fluid does not yet pass through the outlet areas 24 and until the minimum speed is reached / or 26 flows out, but is directed into the lower wing area 12. Since the flow guide device forms a valve device, the supply to the lower wing area 12 can be improved at particularly low pump speeds.
  • the valve elements 33 and 34 are part of a flat resistance structure 30, which can be designed in particular as a thin ring structure as in the exemplary embodiment.
  • the resistance structure 30 can, as in the exemplary embodiment, be flat or shell-shaped. It can, in particular, be made of spring steel or also of other metals, in principle also of a plastic material, as long as the respective material enables the form-elastic valve elements 33 and / or 34 to be formed.
  • the stops 41 and 42 are components of a stop structure 40, which is also included in the flow control device.
  • the stop structure 40 is a two-dimensional structure, in the exemplary embodiment a ring structure. In the exemplary embodiment, it is flat in the form of an annular disk, but in principle it can also be shell-shaped in adaptation to the flow guide structure 20, the resistance structure 30 also being shaped in such a manner in such embodiments.
  • the flow guide device 20, 30, 40 has a layered structure, as in the second and third exemplary embodiments; in contrast to these two exemplary embodiments, it has the stop structure 40 as an additional layer.
  • the resistance structure 30 bears against the end face of the end plate 4.
  • the stop structure 40 is arranged axially between the resistance structure 30 and the flow guide structure 20 arranged axially on the outside.
  • the flow guide structure 20 holds the multi-part flow guide device 20, 30, 40 on the end plate 4 in the positioning engagement of the positioning elements 17 and positioning counter-elements 27, as in the other exemplary embodiments.
  • the resistance structure 30 and the stop structure 40 can also be in a positioning engagement with the same positioning elements 17 to position these two structures in the circumferential direction relative to the respective pressure passage 14 and supply passage 15.
  • FIGS 15 to 17 show a vane pump with a flow control device of a fifth embodiment.
  • the vane pump corresponds to that on the basis of FIG Figures 1 to 5 Pump described, so that reference is made to the statements there and the same reference numerals are used for the same pump components.
  • the flow guide device of the fifth exemplary embodiment comprises a flow guide structure 20 which corresponds to the flow guide structure 20 of the first exemplary embodiment.
  • the flow guide device comprises a resistance structure 30 and a stop structure 40 ( Figures 16 and 17 ), which correspond to the respective first outlet area 24 of the resistance structure 30 and the stop structure 40 of the fourth exemplary embodiment, that is to say form an valve corresponding to the fourth exemplary embodiment in axial overlap with the respective pressure passage 14.
  • the resistance structure 30 and the stop structure 40 are extended radially outward so that, as in the third exemplary embodiment ( Figures 9 to 11 ) immediately upstream of the respective second outlet region 26 form a resistance surface 32, which lengthen the respective third flow path P3 and thus increase its flow resistance in relation to the flow resistance of the second flow path P2.
  • a valve as in the fourth or fifth exemplary embodiment and in the respective third flow path P3, preferably immediately upstream from the respective second outlet region 26, can have a diaphragm with passages 31 as in the second exemplary embodiment instead of a resistance surface 32 in the respective first flow path P1 ( Figures 6 to 8 ) be provided.
  • a plurality of movable valve elements of this type can be provided next to one another in the circumferential direction in the first flow path P1 upstream from the respective first outlet area 24.
  • the resistance structure 30 and the stop structure 40 upstream of the respective first outlet region 24 in the first flow path P1 can form an orifice with one or more passages 31 or instead a resistance surface 32 and one or more valves each with a movable valve element 34 upstream from the respective one second outlet region 26 can be formed in the respective third flow path P3.
  • the different measures for increasing the resistance of the first flow path P1 and / or the second flow path P3 can also be implemented in combinations other than those illustrated for the exemplary embodiments.
  • the resistance structures 30 of the second, third, fourth and fifth exemplary embodiment can be produced in particular by stamping.
  • the passageways 31 can be punched passageways.
  • the passages 31 are circular in the second and third exemplary embodiments, but could also have an oval shape or a slot-shaped or cross-shaped cross-section instead, wherein slot-shaped cross-sections can be straight or curved when viewed in the axial plan view.
  • the passages 31 can be axially cylindrical. Instead, they can also widen or narrow in the direction of flow, for example be trumpet-shaped or bell-shaped or in particular conical.
  • the passages 31 also do not have to be rotationally symmetrical. For example, they can be shaped in such a way that they impart a directional component to the pressure fluid transversely to the axial direction when flowing through, in order to direct the pressure fluid, for example, towards one of the supply passages 15 when flowing through the resistance structure.
  • valve elements 33 and 34 of the fourth and fifth exemplary embodiments can be manufactured by stamping a resistance blank and thus as stamped valve elements. By punching, the valve elements 33 and 34 can be easily released in the form of a spiral spring tongue.
  • the valves of the fourth and fifth exemplary embodiments are each formed in the manner of a reed valve.
  • the stop structure 40 can be shaped in adaptation to the resistance structure 30 as a simple disk or ring which has a small axial distance from the rear side of the resistance structure 30, so that the valve elements 33 and / or 34 formed as spiral spring tongues when elastic Giving in against the modified stop structure comes into stop contact, whereby this stop contact does not have to be full-area and also not flat, but rather is linear or can only take place in a smaller area of the respective valve element 33 and / or 34.
  • FIGS. 18 to 21 show a vane pump with a flow control device of a sixth embodiment.
  • the vane pump corresponds to the pumps described above, so that in particular the explanations for the Figures 1 to 5 referenced and the same reference numerals are used for the same pump components.
  • the flow guide device of the sixth exemplary embodiment comprises a flow guide structure 20 which corresponds to the flow guide structure 20 of the other exemplary embodiments.
  • the flow guide device comprises a resistance structure 30, each with an elastomer valve 36 arranged in the first flow path P1 and in each case with an elastomer valve 37 arranged in the third flow path P3.
  • the resistance structure 30 also includes, as best in FIG Figure 19 recognizable, a support structure 35, on which the elastomer valve elements 36 and 37 are elastically bendable in the axial direction outwards, away from the end plate 4.
  • the elastomer valve elements 36 and 37 are formed as elastomer spring tongues which protrude in the circumferential direction and accordingly bend around radial axes when they bend due to the pressure of the pressure fluid prevailing in the flow guide region.
  • the elastomer valve elements 36 and 37 basically have a comparable effect to the valve elements 33 and 34.
  • a stop structure 40 is not provided.
  • the flow cross section of the elastomer valve formed with the respective elastomer valve element 36 and 37 is thus only determined by the pressure force of the pressure fluid acting on the respective elastomer valve element and the structurally predetermined elastic restoring force of the respective elastomer element.
  • FIGS. 22 to 25 show a vane pump with a flow control device of a seventh embodiment. With the exception of the flow control device, this corresponds to Vane pump of the pump of the other exemplary embodiments, so that reference is made in this regard to the above statements and the same reference numerals are used for the same pump components.
  • the flow guiding device of the seventh exemplary embodiment comprises a flow guiding structure 20 which corresponds to the flow guiding structure of the other exemplary embodiments.
  • the flow guide device comprises a resistance structure 30, which is different from the resistance structure 30 of the sixth exemplary embodiment ( Figures 18 to 21 ) was developed further.
  • the resistance structure 30 of the seventh exemplary embodiment has elastomer valves with elastomer valve elements 38 and 39 arranged distributed around the axis of rotation R.
  • a plurality of elastomer valves with elastomer valve elements 38 and 39 are arranged both in the first flow path P1 upstream from the first outlet region 24 of the respective flood and in the third flow path P3 upstream from the second outlet region 26 of the respective flood.
  • the resistance structure 30 of the seventh embodiment comprises the same carrier structure 35 as the resistance structure of the sixth embodiment.
  • the elastomer valve elements 38 and 39 which are made of an elastomer, are molded onto the support structure 35 as in the sixth exemplary embodiment, so that they can be elastically bent away from the root plate 4 from a root area or molding area.
  • a stop structure is also not provided in the seventh embodiment.
  • the flow guide device consists of the flow guide structure 20 and the resistance structure 30.
  • the carrier structure 35 can be made from a metallic material. But it can also be made of a plastic.
  • the elastomer valve elements 36 and / or 37, as well as the elastomer valve elements 38 and / or 39, can, as already mentioned, be integrally formed on the support structure 35 or be integrally joined to it.
  • the carrier structure 35 and the elastomer valve elements 36 and / or 37 of the sixth exemplary embodiment and the elastomer valve elements 38 and / or 39 of the seventh exemplary embodiment can also be produced together from an elastomeric material, optionally also from natural rubber, and the respective elastomeric valve element by one Post-processing, in particular by means of a separation process, on which a resistance structure is first formed in one piece.
  • the elastomer valve elements 36 to 39 are designed as spring tongues that come from a root area in Protrude circumferential direction.
  • the elastomer valve elements 38 and / or 39 of the seventh exemplary embodiment which are slim in the circumferential direction, can instead also protrude radially from the support structure 35 and accordingly be bent around a tangential axis and thereby be bendable away from the end plate in the open position.
  • the flow guide structure 20 can also provide an increased flow resistance in the first flow path P1 and / or in the third flow path P3 in an integrated design, so that a resistance structure 30 manufactured separately from the flow guide structure 20 can be omitted.
  • the correspondingly modified flow guide structure 20 can be formed in the first outlet region 24 of the respective flood and / or in the second outlet region 26 of the respective flood, for example as an orifice plate with a plurality of passages 31 which are smaller in comparison to the respective outlet region 24 and / or 26.
  • the flow guide structure 20 can also form the stops for the movable valve elements, so that a separately manufactured stop structure can be omitted.
  • the elastomer valve elements 36 and 37 of the sixth exemplary embodiment and / or the elastomer valve elements 38 and 39 of the seventh exemplary embodiment on the flow guide structure 20 in the first outlet region 24 and in the second outlet region 26 of the respective flood, so that the resistance structure 30 of these exemplary embodiments is omitted can. If the resistance structure 30 were omitted, the increased resistance would not be obtained in the flow path P1 and / or P3 upstream from the respective outlet area 24 and / or 26, but directly in the respective outlet area 24 and / or 26.
  • separate production offers advantages in terms of costs and also with regard to the possibilities of flow conduction in the flow control area.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
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  • Rotary Pumps (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
EP17177916.8A 2016-06-30 2017-06-26 Flügelzellenpumpe mit druckbeaufschlagbarem unterflügelbereich Active EP3263835B1 (de)

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CN107559187B (zh) 2019-11-12
DE102016211913A1 (de) 2018-01-18
EP3263835A1 (de) 2018-01-03
CN107559187A (zh) 2018-01-09
US10633972B2 (en) 2020-04-28
US20180003176A1 (en) 2018-01-04

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