WO2014096202A2 - Pompe à piston rotatif - Google Patents

Pompe à piston rotatif Download PDF

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Publication number
WO2014096202A2
WO2014096202A2 PCT/EP2013/077408 EP2013077408W WO2014096202A2 WO 2014096202 A2 WO2014096202 A2 WO 2014096202A2 EP 2013077408 W EP2013077408 W EP 2013077408W WO 2014096202 A2 WO2014096202 A2 WO 2014096202A2
Authority
WO
WIPO (PCT)
Prior art keywords
outflow
rotary piston
pump
channel
piston 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.)
Ceased
Application number
PCT/EP2013/077408
Other languages
German (de)
English (en)
Other versions
WO2014096202A3 (fr
Inventor
Christian Langenbach
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to CN201380073471.9A priority Critical patent/CN105074131B/zh
Publication of WO2014096202A2 publication Critical patent/WO2014096202A2/fr
Publication of WO2014096202A3 publication Critical patent/WO2014096202A3/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/04—Feeding by means of driven pumps
    • F02M37/043—Arrangements for driving reciprocating piston-type pumps
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/04—Feeding by means of driven pumps
    • F02M37/041—Arrangements for driving gear-type pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M37/00—Apparatus or systems for feeding liquid fuel from storage containers to carburettors or fuel-injection apparatus; Arrangements for purifying liquid fuel specially adapted for, or arranged on, internal-combustion engines
    • F02M37/04—Feeding by means of driven pumps
    • F02M37/08—Feeding by means of driven pumps electrically driven
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0001—Fuel-injection apparatus with specially arranged lubricating system, e.g. by fuel oil

Definitions

  • the present invention relates to a rotary piston pump according to the preamble of claim 1, a method for producing at least one rotary piston pump according to the preamble of claim 7 and a high-pressure injection system according to the preamble of claim 14.
  • Rotary piston pumps with electric motor are used for various technical applications for pumping a fluid.
  • prefeed pumps serve as fuel pumps for conveying fuel to a high-pressure pump.
  • the gerotor pumps in this case have an inflow channel, which opens into an inflow working space to introduce the fluid to be conveyed into the inflow work space and an outflow channel, which opens into a Abströmarbeitsraum to the fluid to be pumped from the
  • the Zuströmarbeitsraum thus represents a suction side of a working space of the gerotor pump and the
  • Abströmarbeitsraum represents a pressure side of the working space.
  • Feed Pump Control Such control of the amount of fuel delivered by the high pressure pump without a metering unit is referred to as Feed Pump Control (FPC).
  • FPC Feed Pump Control
  • Gear pump with a plurality of closed conveyor cells known whose volume changes during a revolution from a minimum to a maximum value and back.
  • the pump is used in particular for fuel delivery of an internal combustion engine.
  • the mouth cross-sections are designed for a promotion without internal compression, but such is created by against axial surfaces of the pump parts applied, check valves forming fixed thrust washers.
  • Hydraulic circuit is assigned, and their common flow through a
  • Control means is changeable, wherein the control means is arranged in a housing part of the displacement machine.
  • Impeller with or without a sickle, and with an electric drive, which is formed by the ring gear is arranged inside a rotor of a brushless electric motor and the rotor adjacent to a stator, wherein the rotor containing the ring gear outside of a bearing or a
  • Sliding bearing is rotatably supported, wherein the stator with respect to the rotor and against the interior of the pump thereby shielded and sealed, the bearing or sliding bearing located between the stator and the rotor is impermeable to liquid and is in each case tightly connected at its two end faces to a closing cover. Disclosure of the invention
  • Rotary piston pump according to the invention for conveying a fluid comprising at least one impeller with conveying elements, of which around a
  • Rotation axis is a rotational movement executable, existing on the impeller working space, which is divided into a Zuströmarbeitsraum and Abströmarbeitsraum, a housing, an opening into the Zuströmarbeitsraum inflow channel for introducing the fluid to be conveyed in the Zuströmarbeitsraum and opening into the Abströmarbeitsraum
  • Rotary piston pump can thus two outflow of the pumped
  • Fluids are provided separately through the first and second outflow channel.
  • different volume flows can thus easily be made available by the rotary piston pump through the first and second outflow channels.
  • the inflow channel and / or the first outflow channel and / or the second outflow channel are formed on at least one insert part.
  • the inflow channel, the first outflow channel and the second outflow channel are formed on only one insert part.
  • At least one positive locking geometry preferably a projection or a recess, is formed on the at least one insert part, so that the at least one insert part in
  • Volumetric flow of the funded through the first and second discharge channel fluid can be provided.
  • a bypass channel is formed from the first outflow channel to the inflow channel and / or the
  • Conveying elements are teeth of a gear and / or the
  • Rotary piston pump is a gear pump, preferably
  • Internal gear pump in particular gerotor pump, and / or the
  • Rotary piston pump comprises a housing and preferably at least one insert part rests on the housing and / or the at least one insert part functions as a sliding bearing, in particular as a thrust bearing, for the at least one impeller.
  • the rotary piston pump comprises an electric motor and the electric motor is integrated in the rotary piston pump, in particular the gear pump, in particular by a rotor of the electric motor forms an impeller, preferably by permanent magnets are installed in the impeller and / or the delivery rate of the rotary piston pump, preferably with integrated
  • Electric motor is controlled and / or regulated, in particular in which the power and / or speed of the electric motor can be controlled and / or regulated and / or the rotary piston pump is made with a method described in this patent application.
  • Rotary piston pump in particular a rotary piston pump described in this patent application, with the steps: provide at least one impeller with conveyor elements, provide a housing, mounting the at least one impeller with conveying elements on the housing, so that at the at least one impeller a working space is formed, which is divided into a Zuströmarbeitsraum and in a Abströmarbeitsraum, and a flowing into the Zuströmarbeitsraum inflow channel for introducing the fluid to be conveyed in the Zuströmarbeitsraum and opening into the Abströmarbeitsraum
  • Abströmarbeitsraum is formed, wherein the outflow channel in a first outflow channel and second outflow channel as separate in the
  • Abströmariasraum opening outflow channels is divided by at least one insert is mounted with the first outflow channel and / or the second outflow channel. At the at least one insert part, for example, the first and second outflow channel are formed.
  • At least one insert is mounted with the inflow channel.
  • Inflow channel, the first outflow channel and the second outflow channel mounted and / or the at least one insert is at least one form fit geometry on the at least one insert form fit to at least one Gegenform gleichgeometrie on the rest
  • Rotary piston pump in particular the housing, fixed and thereby the position, in particular rotational angle position, of the at least one insert part with respect to the other rotary piston pump, in particular the working space fixed.
  • Housings mounted, so that the first and second outflow channels at different positions, in particular rotational angular positions, to the
  • Inserts are in different positions, in particular
  • Outflow channel is arranged at a different position at the Abströmarbeitsraum. This makes it possible in a simple manner only or substantially only by the fact that the inserts are arranged at different positions to the rest of the rotary piston pump, different rotary piston pump with a different ratio of
  • Rotary piston pumps are manufactured in a simple manner. This makes it possible to inexpensively produce such rotary piston pumps.
  • insert parts with at least one form fit geometry at least one
  • Rotary piston pump is formed at least one Jacobson gleichgeometrie. This is, for example, a hole as
  • the identical inserts can be attached to the positive engagement geometries at different positions with respect to the rest of the rotary piston pump.
  • the first and second outflow ducts are also arranged on the insert part in different positions on the outflow working space, so that this is different only because of the different positioning of the insert part Rotary piston pumps with a different ratio of
  • Volumetric flow which is conveyed through the first and second outflow, can be produced.
  • different inserts are mounted on the inserts with a different position of the at least one interlocking geometry, and due to different positions of the at least one interlocking geometry, the inserts become
  • this recess needs to be stamped as positive locking geometry of the insert only at different positions on the insert and then this insert with the punched as a recess on a Projection can be attached to the housing in different positions.
  • the inserts can for example be easily manufactured as stampings made of metal plates. For this only need different first and second outflow channels are punched into the inserts and these different inserts can otherwise be attached to substantially identical rotary piston pumps and thus can only by the use and assembly of these
  • the at least one insert is produced by punching.
  • Rotary piston pump is designed as a rotary piston pump described in this patent application.
  • a high-pressure injection system according to the invention for an internal combustion engine comprising a high-pressure pump, a high-pressure rail, a prefeed pump for conveying a fuel from a fuel tank through a first fuel line to an inlet channel of the high-pressure pump and through a second fuel line to a lubrication chamber of the high-pressure pump, wherein the prefeed pump as an in described in this patent application
  • High-pressure pump is formed and a first of the two outflow channels of the rotary piston pump opens into the first fuel line and a second of the two outflow channels of the rotary piston pump opens into the second fuel line.
  • Outflow channels provided so that constantly at least one
  • Conveying element of the impeller seals within the Abströmarbeitsraumes a discharge channel of the other outflow channel. Pressure surges on one outflow channel do not reach the other outflow channel.
  • Substantially no fluid-conducting connection preferably means that in
  • the internal gear pump comprises an internal gear having an internal gear and an external gear having an external gear, wherein the teeth of the internal gear mesh with the teeth of the external gear and the working space is formed between the internal gear and the external gear.
  • the internal gear is mounted eccentrically to the external gear.
  • the amount, in particular the volume, of the fluid delivered by the two outflow passages varies per revolution of the at least one impeller, in particular the amount of fluid passed through the first outflow passage is greater than the amount of fluid passed through the second outflow passage.
  • Fuel line. Pressure surges in the lubricating space thereby do not reach the inlet valve of the high-pressure pump and even with pressure surges within the lubricating space due to the oscillating movement of the piston of the high pressure pump is characterized the function of the high-pressure pump on the
  • Rotary piston pump is designed to the effect that in any position of the impeller of the rotary piston pump substantially no fluid-conducting Connection between the two outflow channels through the Abströmarbeitsraum the rotary piston pump consists.
  • the gears of the gerotor pump constantly separate the Abströmarbeitsraum at the first outflow from the Abströmarbeitsraum at the second
  • Substantially no fluid-conducting connection between the first and second fuel line preferably means that during operation of the rotary piston pump at pressure differences between the first and second outflow channel or between the first and second fuel line less than 30%, 20%, 10%, 5% or 2 % of the fluid flows through the Abströmarbeitsraum due to the pressure difference between the first and second outflow channel than would flow through the Abströmarbeitsraum, if the
  • the rotary piston pump is a rotary vane pump, a rotary lobe pump or a centrifugal pump.
  • the rotary piston pump with, preferably integrated, electric motor comprises a, preferably electronic, control unit for controlling the energization of the electromagnets and / or the electric motor is a brushless or electronically commutated electric motor.
  • Suitably consists of the housing of the rotary piston pump and / or the housing of the high pressure pump and / or the inner and / or outer gear at least partially, in particular completely, made of metal, for. As steel or aluminum.
  • FIG. 1 shows a cross section of a high-pressure pump for conveying a fluid
  • FIG. 2 shows a section AA according to FIG. 1 of a roller with roller shoe and a drive shaft
  • 3 is a highly schematic view of a high-pressure injection system
  • Fig. 4 is a greatly simplified cross-section of the high pressure pump
  • FIG. 5 is a perspective view of a prefeed pump without housing and a stator
  • Fig. 6 is an exploded view of the prefeed pump according to FIG. 5 with
  • Fig. 7 shows a cross section of an inner and outer gear of
  • Fig. 8 is a side view of an insert in a
  • 9 is a side view of an insert in a
  • Fig. 10 is a greatly simplified longitudinal section of the prefeed pump
  • Fig. 5 and 6 and Fig. 1 1 is a greatly simplified longitudinal section of the feed pump
  • Fig. 1 is a cross section of a high-pressure pump 1 for conveying fuel is shown.
  • the high-pressure pump 1 serves to fuel, z. As gasoline or diesel, to promote a combustion engine 39 for a motor vehicle under high pressure.
  • the maximum pressure that can be generated by the high-pressure pump 1 is, for example, in a range between 1000 and 3000 bar.
  • the high-pressure pump 1 has a drive shaft 2 with two cams 3, which performs a rotational movement about a rotation axis 26.
  • the axis of rotation 26 lies in the plane of the drawing of FIG. 1 and is perpendicular to the
  • a piston 5 is mounted in a cylinder 6 as a piston guide 7, which is formed by a housing 8 of the high-pressure pump 1.
  • High-pressure working chamber 29 is bounded by the cylinder 6 as a piston guide 7, the housing 8 and the piston 5.
  • the high-pressure working chamber 29 opens an inlet channel 22 with an inlet valve 19 and an outlet channel 24 with an outlet valve 20.
  • the fuel flows into the high-pressure working chamber 29 and through the
  • Working space 29 can flow out.
  • the volume of the high-pressure working chamber 29 is changed due to an oscillating stroke movement of the piston 5.
  • the piston 5 is indirectly supported on the drive shaft 2 from.
  • a roller shoe 9 is attached to a roller 10.
  • the roller 10 can perform a rotational movement, the
  • Rotation axis 25 lies in the plane of FIG. 1 and is perpendicular to the plane of Fig. 2.
  • the drive shaft 2 with at least two cams 3 has a shaft rolling surface 4 and the roller 10 has a roller rolling surface 11.
  • roller tread 1 1 of the roller 10 rolls on the shaft rolling surface 4 as a contact surface 12 of the drive shaft 2 with the two cams 3 from.
  • Roller shoe 9 is mounted in a roller shoe bearing formed by the housing 8 as a sliding bearing.
  • Rolling surface 4 of the drive shaft 2 is.
  • the roller shoe 9 and the piston 5 thus carry out together an oscillating stroke movement.
  • the roller 10 is mounted with a sliding bearing 13 in the roller shoe 9.
  • Fig. 3 is a highly schematic representation of a high-pressure injection system 36 for the motor vehicle (not shown) imaged with a high-pressure rail 30 or a fuel rail 31.
  • An electric prefeed pump 35 delivers fuel from a fuel tank 32 through a first fuel line 33a to the intake passage 22 and through a second fuel passage 33b to a lubricating space 40 (FIG. 4)
  • High-pressure pump 1 The high-pressure pump 1 is driven by the drive shaft 2 and the drive shaft 2 is a shaft, for. As a crank or
  • the delivery rate of the electric prefeed pump 35 is controllable and / or controllable, so that thereby the delivered to the inlet channel 22 amount of fuel can be controlled and / or regulated.
  • the high-pressure rail 30 serves to fuel in the
  • High-pressure pump 1 unused fuel is returned through an optional fuel return line 34 back into the fuel tank 32.
  • Fig. 4 shows a part of the high-pressure injection system 36.
  • Lubrication chamber 40 the drive shaft 2, the roller 10, the roller shoe 9 (not shown in Fig. 4) and partially the piston 5 is arranged.
  • these components 2, 5, 9 and 10 are lubricated by the fuel.
  • the introduced through the second fuel line 33 b in the lubricating chamber 40 fuel is through the
  • Fuel tank 32 fed back (Fig. 4).
  • the high pressure injection system 36 shown in Fig. 3 is shown in more detail without the high pressure rail 30 and without the engine 39.
  • the sucked by the prefeed pump 35 from the fuel tank 32 fuel is supplied from the prefeed pump 35 with a prefeed, z. B. 4 bar, supplied through the first fuel line 33 a the inlet channel 22 of the high-pressure pump 1. Furthermore, the fuel delivered by the prefeed pump 35 during operation of the
  • Piston 5 After flowing through the fuel through the lubricating space 40th the fuel is returned to the fuel tank 32 through the fuel return line 34. As a result, these components 2, 5, 9 and 10 can be lubricated as well as cooled.
  • the prefeed pump 35 thereby promotes not only the flow rate for the high-pressure pump 1 to fuel but also an additional amount of fuel for lubrication of the high-pressure pump 1, ie the fuel flowing through the lubricating space 40.
  • the electric prefeed pump 35 has an electric motor 17 and a
  • Rotary piston pump 16 namely a gear pump 14, d. H. a
  • the high-pressure pump 1 delivers fuel under high pressure, for example, a pressure of 1000, 3000 or 4000 bar, through a high pressure fuel line to a high pressure rail 31. From the high pressure rail 31 of the fuel under high pressure from an injector combustion chamber (not shown) of
  • the electric motor 17 (FIGS. 5 and 6) of the electric prefeed pump 35 is operated with three-phase current or alternating current and can be controlled and / or regulated in terms of power and thus also in terms of rotational speed.
  • the three-phase current or alternating current for the electric motor 17 is from a power electronics, not shown from a
  • the electric prefeed pump 35 is thus an electronically commutated prefeed pump 35.
  • the electric prefeed pump 35 or gerotor pump 15 has a housing 42 as a rotary piston pump housing 42 with a housing pot 44 and a housing cover 43 (FIG. 6).
  • the gerotor pump 15 as an internal gear pump 15 and gear pump 14 and the electric motor 17 are arranged.
  • the housing pot 44 is provided with a recess 72.
  • the electric motor 17 has a stator 47 with
  • the gerotor pump 15 is positioned as an internal gear pump 15 having an internal gear 56 with an internal gear ring 57 and an external gear 58 with an external gear ring 59.
  • the inner and outer gears 56, 58 thus represents a gear 54 and an impeller 52 and the inner and Outer ring 57, 59 have teeth 55 as conveying elements 53.
  • a working space 62 is formed between the inner and outer gear 56, 58.
  • permanent magnets 51 are installed, so that the
  • Electric motor 17 is thus integrated into the gerotor pump 15 and vice versa.
  • Electromagnets 49 of the stator 47 are alternately energized, so that due to the magnetic field generated at the electromagnet 49, the rotor 50 or the external gear 58 is set in a rotational movement about a rotation axis 61.
  • the housing cover 43 serves as a bearing 45 or thrust bearing 45 or plain bearing 45 for the inner or outer gear 56, 58.
  • the housing pot 44 and the housing cover 43 each have three holes 71, in which not shown screws for screwing together the housing pot 44 and the housing cover 43 are positioned, with a not shown
  • the recess 72 on the housing pot 44 serves to at the recess 72 electrical contact elements or lines to the
  • FIG. 7 the cross section of the internal gear 56 and the external gear 58 of the gerotor pump 15 is shown. Between the internal gear 56 and the external gear 58, the working space 62 of the internal gear pump 15 is formed. If the inner and outer gears 56, 58 are rotated counterclockwise, with the inner and outer gears 56, 58 being eccentrically mounted to each other, forms on the inner and outer gears 56, 58, d. H.
  • Working space 62 is the Abströmarbeitsraum 64, in which the working space 62 is reduced and thereby a pressure side of the
  • Internal gear pump 15 is formed.
  • Zuströmarbeitsraum 63 opens an inflow channel 65, which is formed on the housing 42 of the internal gear pump 15.
  • the inflow channel 65 has a Wnkel Scheme 18 of less than 180 °.
  • the Abströmarbeitsraum 64 opens a first Outflow channel 66 and a second outflow channel 67, each with an angular range 46.
  • the inflow channel 65 and the first and second outflow channel 66, 67 are shown in Fig. 7 each dashed lines. From the Abströmarbeitsraum 64 can thus be derived hydraulically separated from the Abströmarbeitsraum 64 by two hydraulically separated outflow channels 66, 67 of the fuel hydraulically separated.
  • the sealing distance or the angular range 75 between the two outflow passages 66, 67 ie the distance between the two outflow passages 66, 67, is chosen such that there is no leakage between the two outflow passages 66, 67, so that in each position of the Internal and external gear 56, 58 no fluid-conducting connection between the two outflow channels 66, 67 is. There is thus essentially no fluid-conducting connection from the second outflow channel 67 to the first outflow channel 66.
  • the fuel passed through the first discharge passage 66 is supplied to an intake valve 19 of the high pressure pump 1 through the first fuel passage 33a, and the fuel passing through the second exhaust passage 67 is supplied to the lubrication space 40 through the second fuel passage 33b (FIG. 4). Due to the lack of fluid-conducting connection from the second outflow channel 67 into the first outflow channel 66 can thereby pressure fluctuations in the lubricating chamber 40, which due to the oscillating movements of the
  • Piston 5 occur in the lubricating space 40, not through the gerotor pump 15 and the first fuel line 33 a to the inlet valve 19 of the
  • the flow rate of the gerotor pump 15 is controllable and / or controllable, since it is driven by a controllable in the power electric motor 17.
  • Outflow channel 67 are formed on a plate-shaped insert 38.
  • the insert 38 rests on one side according to the embodiment in Figs. 6 and 10 on the housing pot 44 and on the other side of the insert 38 are the internal gear 56, the outer gear 58 and the stator 47, so that the other side of the insert 38 is also an axial sliding bearing 45 for the
  • the insert 38 is made of metal, for. B. Steel or aluminum, prepared and preferably has a plain bearing coating.
  • the insert 38 as shown in Figs. 8 and 9 and in Figs. 6 and 10 is circular in cross-section and due to a likewise circular in cross-section recess on the housing pot 44, the insert 38 is located at its outer edge on the
  • Housing pot 44 and is thereby fixed perpendicular to the axis of rotation 61.
  • the insert 38 has on the side which rests on the housing pot 44, a form-fitting geometry 41 as a projection 76, z. B. as a retaining pin, and the housing pot 44 has aellesform gleichgeometrie 60 a recess 77 as a bore.
  • the projection 76 on the insert 38 is within the
  • the insert 38 shown in Fig. 8 and 10 thus has the first and second outflow channel 66, 67, which open into the Abströmarbeitsraum 64 as a working space 62 and the
  • Inflow channel 65 which opens into the Zuströmarbeitsraum 63 as a working space 62.
  • a sealing groove 79 is further provided, in which a seal 80, z. B. is arranged as an O-ring seal, so that thereby the housing lid 43 resting on the housing cover 43 fluid-tight closes the housing pot 44 and is connected thereto.
  • housing pot 44 an inflow opening 81, a first outflow opening 82 and a second outflow opening 83 are formed.
  • the inflow opening 81 opens through an inflow bore into the inflow channel 65 defined by the insert 38 and the first outflow opening 82 opens or is fluid-conductively connected by a first outflow bore to the first outflow channel 66.
  • the second outflow opening 83 is defined by a second inflow opening 83
  • Rotary piston pumps 16 produce, which have a different ratio of the volume flow of the funded through the first and second discharge channel 66, 67 fluid.
  • the rotary piston pump 16 as
  • Gear pump 14 is, for example, as Vor fundamentalpumpe 35 in a High-pressure injection system 36 used. In such
  • High-pressure injection systems 36 for different internal combustion engines 39 and motor vehicles it can for optimal adaptation of the to
  • High pressure pump 1 and funded by the lubricant chamber 40 fuel may be required to provide different flow rates available.
  • Abströmkanal 66, 67 produce in order to adjust these flow rates optimally to the requirements of different internal combustion engines 39 can.
  • Drill housing pot 44 When inserting the insert 38 can thereby insert part 38 at different angles of rotation with respect to the
  • Housing pot 44 thereby be particularly cost-effectively fixed and only thereby can different gear pumps 14 with a
  • the first and second outflow holes which open into the first and second outflow channel 66, 67, can be produced either at identical positions, provided nevertheless a fluid-conducting
  • Connection to the first and second outflow channel 66, 67 consists.
  • first and second outflow bores can also be worked into the housing pot 44 at different positions in adaptation to the position of the recess 77.
  • the internal gear 56 is as in
  • the Insert 38 is disposed between the housing cover 43 and the housing pot 44 and not within a recess on the housing pot 44 as in the embodiment in Fig. 10.
  • the insert 38 is thus visible on the outside of the housing 42 and thereby partially also forms the housing 42nd
  • the seal is made, as in the embodiment in Fig. 10, with a plurality of sealing grooves 79 with seals 80.
  • the housing 42 as
  • Housing cover 43 has a projection 76 as counter-form-fitting geometry 60, which engages in a positive-locking geometry 41 as a recess 77 on the insert 38, so that thereby the insert 38 in his
  • the recess 77 may
  • Fig. 11 may be incorporated as a bore or as a punch in a manufacture of the insert 38 by means of punching.
  • the recess 77 By incorporating the recess 77 at different positions of the insert 38 with respect to the first and second outflow 66, 67 of the first and second outflow channel 66, 67 can be arranged at different rotational angle positions with respect to Abströmarbeitsaumes 64 and thereby different flow rates of the first and second Outflow channels 66, 67 conducted fluid can be produced. It is thus possible in a simple manner to produce gear pumps 14 only by the incorporation of recesses 77 in different positions on the insert 38 with a different volume flow, which is derived through the first and second outflow opening 82, 83. The production of
  • Gear pumps 14 with such different volume flows at the first and second outflow openings 82, 83 is thereby particularly inexpensive.
  • Outflow channel 66 incorporated to the inflow channel 65. In a downhill driving the motor vehicle continues to promote fuel through the second outflow channel 67 through the lubricating space 40, but no fuel through the first
  • the gear pump 14 Downhill, the gear pump 14 is operated only at a very low speed and it is also only a small flow through the
  • Gear pump 14 thus constantly passes fuel from the first outflow channel 66 to the inflow passage 65 through the bypass passage 37. However, it is at larger flow rates or speeds of the gear pump 14 by the
  • Bypass channel 37 guided fuel in its flow negligible compared to the remaining volume flow, which to the
  • High-pressure pump 1 is passed.
  • the bypass channel 37 may also be formed outside the gear pump 14 (FIGS. 3 and 4).
  • Insert 38 in an analogous manner as in the embodiment in Fig. 10 and 1 1 by means of a positive connection geometry 41 and a
  • first and second outflow ducts 66, 67 are stamped into the insert 38 in a different size and / or in a different angular range, so that such
  • gear pumps 14 can be produced only by insert parts 38 are made with different first and second outflow channels 66, 67 by means of punching. Overall, significant advantages are associated with the rotary piston pump 16 according to the invention and the high-pressure injection system 36 according to the invention. It can easily gear pumps 14 with a different volume flow, which through the first and second
  • Outflow channel 66, 67 is conveyed, are produced. Due to the low production costs of such prefeed pumps 35 as gear pumps 14 with the different volume flows at the first and second Outflow channel 66, 67, this particular volume flow can thus be optimally adapted to the correspondingly required volume flow for the high-pressure pump 1 and the lubricating chamber 40 particularly precisely with a low cost, because thereby no or substantially no higher costs incurred in the preparation of the gear pump 14th

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Rotary Pumps (AREA)
  • Details Of Reciprocating Pumps (AREA)
  • Reciprocating Pumps (AREA)

Abstract

L'invention concerne une pompe à piston rotatif (16) servant au refoulement d'un fluide et comprenant au moins une roue mobile (52) munie d'éléments de refoulement (53) qui permettent l'exécution d'un mouvement de rotation autour d'un axe de rotation (61), un espace de travail ménagé au niveau de la roue mobile (52) et divisé en un espace de travail d'entrée et un espace de travail de sortie, un carter (42), un canal d'entrée débouchant dans l'espace de travail d'entrée et servant à introduire le fluide à refouler dans l'espace de travail d'entrée, et un canal de sortie débouchant dans l'espace de travail de sortie et servant à évacuer le fluide à refouler hors de l'espace de travail de sortie. La pompe à piston rotatif (6) comporte un premier canal de sortie et un deuxième canal de sortie sous la forme de canaux de sortie débouchant séparément dans l'espace de travail de sortie.
PCT/EP2013/077408 2012-12-20 2013-12-19 Pompe à piston rotatif Ceased WO2014096202A2 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201380073471.9A CN105074131B (zh) 2012-12-20 2013-12-19 旋转式活塞泵

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102012223907.3 2012-12-20
DE102012223907.3A DE102012223907B4 (de) 2012-12-20 2012-12-20 Verfahren zur Herstellung wenigstens einer Rotationskolbenpumpe und einHochdruckeinspritzsystem

Publications (2)

Publication Number Publication Date
WO2014096202A2 true WO2014096202A2 (fr) 2014-06-26
WO2014096202A3 WO2014096202A3 (fr) 2014-09-18

Family

ID=49917061

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2013/077408 Ceased WO2014096202A2 (fr) 2012-12-20 2013-12-19 Pompe à piston rotatif

Country Status (3)

Country Link
CN (1) CN105074131B (fr)
DE (1) DE102012223907B4 (fr)
WO (1) WO2014096202A2 (fr)

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US12378915B2 (en) * 2020-01-27 2025-08-05 Safran Helicopter Engines Fuel supply circuit of an aircraft engine

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102015213387A1 (de) * 2015-07-16 2017-01-19 Robert Bosch Gmbh Rotationskolbenpumpe
CN107100676B (zh) * 2017-05-04 2020-11-06 张定强 一种旋转活塞式轮机
CN112032201B (zh) * 2020-09-01 2022-05-03 中国重汽集团济南动力有限公司 一种主销衬套动力润滑结构

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DE3406349A1 (de) 1983-06-03 1984-12-06 Robert Bosch Gmbh, 7000 Stuttgart Verdraengermaschine
DE3624532C2 (fr) 1986-07-19 1989-09-28 Pierburg Gmbh, 4040 Neuss, De
DE29913367U1 (de) 1999-07-30 1999-12-09 Pumpenfabrik Ernst Scherzinger GmbH & Co. KG, 78120 Furtwangen Innen-Zahnradpumpe, deren Hohlrad das Innere eines Rotors eines Elektromotors ist

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US2368883A (en) * 1942-12-12 1945-02-06 Pesco Products Co Multiple discharge pump
JPH05263770A (ja) * 1992-03-24 1993-10-12 Unisia Jecs Corp オイルポンプ
DE4303328C2 (de) 1993-02-05 2001-11-29 Mannesmann Vdo Ag Gerotorpumpe zum Fördern von Fluid, insbesondere als Kraftstoff-Förderaggregat für Kraftfahrzeuge
JP3531769B2 (ja) * 1994-08-25 2004-05-31 アイシン精機株式会社 オイルポンプ装置
EP1803938A1 (fr) 2005-12-27 2007-07-04 Techspace Aero S.A. Groupe motopompe hautement intégré à moteur électrique
DE102006056844A1 (de) 2006-12-01 2008-06-05 Robert Bosch Gmbh Innenzahnradpumpe
DE102009047709A1 (de) * 2009-12-09 2011-06-16 Robert Bosch Gmbh Zahnradpumpe
DE102010062668A1 (de) * 2010-12-08 2012-06-14 Robert Bosch Gmbh Kraftstofffördersystem einer Brennkraftmaschine, mit einer Rotationspumpe
DE102011076025A1 (de) 2011-05-18 2012-11-22 Robert Bosch Gmbh Pumpe mit Elektromotor

Patent Citations (3)

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Publication number Priority date Publication date Assignee Title
DE3406349A1 (de) 1983-06-03 1984-12-06 Robert Bosch Gmbh, 7000 Stuttgart Verdraengermaschine
DE3624532C2 (fr) 1986-07-19 1989-09-28 Pierburg Gmbh, 4040 Neuss, De
DE29913367U1 (de) 1999-07-30 1999-12-09 Pumpenfabrik Ernst Scherzinger GmbH & Co. KG, 78120 Furtwangen Innen-Zahnradpumpe, deren Hohlrad das Innere eines Rotors eines Elektromotors ist

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US12378915B2 (en) * 2020-01-27 2025-08-05 Safran Helicopter Engines Fuel supply circuit of an aircraft engine

Also Published As

Publication number Publication date
DE102012223907B4 (de) 2022-12-01
WO2014096202A3 (fr) 2014-09-18
CN105074131A (zh) 2015-11-18
CN105074131B (zh) 2018-06-26
DE102012223907A1 (de) 2014-06-26

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