EP0843096B1 - Koppeleinrichtung zwischen einer Kraftstoff-Förderpumpe und einer Luft fördernden Pumpe in einem Gehäuse angeordnet - Google Patents
Koppeleinrichtung zwischen einer Kraftstoff-Förderpumpe und einer Luft fördernden Pumpe in einem Gehäuse angeordnet Download PDFInfo
- Publication number
- EP0843096B1 EP0843096B1 EP97115817A EP97115817A EP0843096B1 EP 0843096 B1 EP0843096 B1 EP 0843096B1 EP 97115817 A EP97115817 A EP 97115817A EP 97115817 A EP97115817 A EP 97115817A EP 0843096 B1 EP0843096 B1 EP 0843096B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pump
- drive shaft
- coupling device
- chamber
- control piston
- 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.)
- Expired - Lifetime
Links
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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
- F02M37/14—Feeding by means of driven pumps the pumps being combined with other apparatus
-
- 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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
- F04C11/005—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations of dissimilar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
- F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
- F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
- F04C18/3441—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, 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 group F04C18/08 or F04C18/22 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 one line or continuous surface substantially parallel to the axis of rotation
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/005—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of dissimilar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2220/00—Application
- F04C2220/10—Vacuum
Definitions
- the invention relates to a device for conveying Fuel from a storage tank to an internal combustion engine of a motor vehicle according to the preamble of claim 1 out.
- Such a device is known from DE 195 13 822 A1 become known from one of the internal combustion engine driven feed pump is formed, the fuel from sucks in a storage tank and to the internal combustion engine or a high-pressure injection pump provided on this promotes.
- the feed pump has at least one in its housing Pump chamber in which a pair of rotating and driven intermeshing gears is arranged, the Fuel from a connectable to the storage tank Intake space along one between the face of the Gears and the wall formed conveyor channel in one at least indirectly connectable to the internal combustion engine Promote pressure room.
- the suction side with a brake booster of the motor vehicle is connected.
- the feed pump and the air pump are coaxial arranged side by side in a common housing and are rotating by a common drive shaft driven.
- the in the common housing of the feed pump Air pump used is preferably as Vane pump designed.
- the preferably as Gear pump designed feed pump is axial arranged one behind the other to the vane pump, so that a driven gear of the feed pump and a rotor of the Vane pump rotating from the common drive shaft are driven.
- the device for conveying fuel according to the invention from a storage tank to an internal combustion engine Motor vehicle with the characteristic features of the Claim 1 has the advantage that the between the feed pump and the air pump arranged coupling device a demand-driven control the air pump can be done. This will due to the air that is not permanently co-powered Pump achieved a reduction in drive power. About that In addition, the device according to the invention has the advantage on that through the need-based actuation of the air promoting pump a reduction in wear at the Component components of the air pump is enabled.
- the Coupling device can be ensured that a Minimum value of negative pressure in the brake booster is present immediately after a braking operation in which the vacuum decreases by turning on the air pump to the required vacuum in the Brake booster can be increased.
- This in Dependence on a certain minimum value of negative pressure working coupling device is particularly effective longer overland trips or freeway trips without one Braking process advantageous.
- the drive shaft can through the axially one behind the other arranged delivery pump and air-producing pump achieved Minimization of the installation space can be maintained. moreover can be used on a variety of existing ones Component components from such a device for Conveying fuel from a storage tank to one Internal combustion engine of a vehicle can be used, where the feed pump and the air pump are in one common pump housing arranged as a structural unit are.
- rotating on the of the feed pump driving drive shaft provided the coupling device is. This allows a small installation space for the device be maintained. Furthermore, an easy one Drive of the coupling device possible to the rotary movement to transfer to the vane pump.
- the coupling device directly with the to the brake booster facing suction side via a Coupling device leading through hole is connected. This can actually be done in a simple manner present negative pressure a control of the Coupling device be given. Thus, without use control of additional components Coupling device may be provided, which when a predetermined negative pressure the positive connection between the feed pump and the air pump separates.
- the coupling device as a slip clutch is formed, which is axially movable to the drive shaft Control piston which is on a clutch disc of the air pump.
- the Coupling device as magnetic or hydraulic or electrically controllable clutch is formed, which receives corresponding control commands via sensors that again the current vacuum in the brake booster can capture.
- control piston of the coupling device has a piston chamber which can be acted upon by vacuum, in the one working against the negative pressure is arranged.
- the stress agent which is preferably called Compression spring element is formed depending on the axial forces acting on the control piston chamber Be adjusted negative pressure, so that from a minimum value Vacuum the spring force can be overcome, making the Control piston opposite the clutch disc of the air pump can be separated. This can cause a Self-regulation can be achieved in which only from one predetermined minimum value of negative pressure which promotes air Pump is switched off.
- the for Through bore leading suction side seen in the suction direction in front of one leading into the intake space and one Non-return valve connecting piece opens. Thereby can control the Coupling device can be achieved, the actual in Brake booster prevailing negative pressure is detected.
- the feed pump can alternatively be used as another Positive displacement pump, e.g. designed as a roller cell pump his.
- the pump housing 1 has a inside circular recess on one end face 9 of the pump housing 1 open pump chamber 7 of the Vane pump 5 forms and the radially inward a cylindrical arranged eccentrically to the pump chamber 7 Housing web 11 is limited.
- In this housing web 11 is an axial through hole 13 is introduced in the one Drive shaft 15 is rotatably guided in the by the End face 9 facing away from the pump housing 1 protrudes.
- Drive shaft 15 On the free end protruding from the pump housing 1 Drive shaft 15 is pressed on a drive plate 17, in the grooves for receiving an elastic coupling member in Form of a feather key 19 are provided.
- the pump housing 1 has the second of the Face plate 21 facing an oval, one Pump chamber of the gear pump 3 forming recess, the is separated from the pump chamber by a partition wall and which is penetrated by the drive shaft 15. It is a first gear 25 one with the other Frontal meshing gear pair on the drive shaft 15 within the pump chamber 23 by means of a Drive shaft 15 pressed pin 27 with a positive fit this connected.
- the second gear, not shown is arranged obliquely to the first gear 25, wherein whose axis is also mounted in the pump housing 1.
- On upper, radially to the gears at the level of Tooth-engaging section of the pump chamber 23 forms a suction chamber 29 and a lower one, this Gear engagement opposite section of the pump chamber 23 a pressure chamber 31 of the gear pump 3.
- suction chamber 29 opens a suction hole in the pump housing 1, which with a Fuel line from the storage tank is connected.
- Pressure chamber 31 discharges a pressure channel 25 through a bead is formed in the end face 21 of the pump housing 1 and which extends into a web 37 of the pump housing 1.
- Parallel to this pressure channel 35 is also a Bead formed return channel 39 is arranged, which via a Connecting bore 41 is connected to the pressure channel 35 and starting from this to about the end of the Pressure channel 35 extends.
- the pump chamber 23, the pressure channel 35 and the return channel 39 are on the housing 1 opposite side by a on the end face 21 of the Pump housing 1 sealingly screwed on first Closed cover 43, in which one of the pressure channel 35 discharge pressure bore 45 and one from the return duct 39 Laxative return bore 47 are arranged.
- the Housing cover 43 in turn to the cylinder head supplying internal combustion engine that the Pressure bore 45 and the return bore 47 directly on corresponding fuel channels open in the cylinder head.
- Vane pump 5 is made from a pump chamber 7 arranged cylindrical rotor 51 with an axial bore formed with its cylindrical inner wall surface 53 in Form of a plain bearing on the lateral surface of the cylindrical housing web 11 is guided.
- the rotor 51 is via an end of the gear pump facing away from the Drive shaft 15 arranged coupling device 52 with a Coupling disc 55 connected, which is on the other hand second, the pump chamber 7 of the vane pump 5 closing housing cover 56 via a bearing means 57 supports the sealing on the end face 9 of the Pump housing 1 is screwed.
- the pump chamber 7 radially inward bounding cylindrical outer wall surface 64 of the rotor 51 are preferably three slots 59 for slidable mounting of wings provided in Direction of rotation of the rotor 51 tilted on its radial plane are. Since the rotor 51 is so eccentric in the pump 7 is arranged so that it partially with its outer wall surface 64th bears against the radial pump chamber wall 63 of the pump chamber 7, the slots 59 are designed so that they are complete Immersion of the wing 61 and sufficient guidance allow maximum immersion, as well as sealing surfaces to the Form wings 61 to pressurize the Rotor 51 located wing ends by the lubricating oil Wing 61 forced radially outwards during the suction phase to press and thus the contact pressure and sealing effect of the Wing 61 on the housing 1, especially at low speeds improve.
- An upper region of the pump chamber 7 forms when the Counterclockwise a suction area 65 the vane pump 5, which in a connection bore 67th opens into which a connecting piece 69 is inserted, on the a hose line from a brake booster Motor vehicle is pluggable.
- the connecting piece 69 in the direction of the pump chamber 7 opening check valve 71 above bore 67 upstream.
- the gear pump 3 and vane pump 5 is on the Coupling device 52 connected by a drive Drive shaft 15 is received.
- the coupling device 52 is designed as a slip clutch, which depending on a Minimum value of vacuum in the brake booster one positive connection of the gear pump 3 to Vane pump 5 separates.
- the coupling device 52 has a spool 91, which is in a spool seat 109 is guided and arranged on the drive shaft 15 Driver elements 92 is driven to rotate.
- the Control piston 91 is simultaneously over the driver elements 92 axially movable to the drive shaft 15 so that a to the clutch disc 55 facing end face 93 on the Clutch disc 55 can engage non-positively.
- the Control piston 91 and the clutch disc 55 are off heat-resistant material, which is beyond is low wear.
- the end face 93 has a high Machining accuracy so that with a complementary Surface of the clutch disc 55 with a slip clutch rapid intervention and high power transmission is given.
- the control piston 91 has a control piston chamber 94 which is designed as a cylindrical blind bore.
- the Control piston chamber 94 is located in the drive shaft 15 trained axial bore 96 in connection, which in a Cross bore 97 merges and opens into an annular groove 98.
- the bores 101 and 102 extend itself up to an end face 103 that extends from a first Housing cover 43 is closed.
- These through holes 101, 102 close an angle of essentially 90 ° to each other, making it easy to manufacture Bores in the pump housing 1 is given.
- the there is at least one transverse bore 97 and the axial bore 96 the control piston chamber 94 directly with a vacuum chamber of the brake booster in connection.
- the clutch disc 55 is designed as a ball Bearing means 57 arranged to the second housing cover 56, whereby the axial acting via the coupling device 52 Forces resulting in a rotational movement of the clutch disc 55 transmitted, added under load with little friction become.
- the driver elements 92 are claw-shaped, as a feather key profile or designed as a spline profile and grip in an equally designed end region of the control piston 91 one facing the drive shaft 15.
- a loading means 104 is arranged, which as Compression spring element is formed.
- the load device 104 is supported in a bore 106 of the drive shaft 15, so that an axial force is exerted on the control piston 91 can, with its end face 93 on the clutch disc 55 attacks.
- the drive shaft 15 faces coaxially Bore 106 an annular collar 107 on which the Driver elements 92 are arranged. Supports at the same time this collar is located opposite the driver elements on the control piston seat 109 of the housing web 11.
- the Piston seat is by fine machining, preferably Rub, made.
- the control piston 91 is sealed with formed its outer surface to the control piston seat 109. Alternatively, it can be provided that the control piston Has sealing ring or the like to a sealing Allow arrangement.
- the conveyor device operates in the following Wise. Drives during operation of the internal combustion engine the drive shaft of the internal combustion engine the drive shaft 15 the conveyor via the elastic coupling on the Driving disk 17 rotating. This rotary movement of the Drive shaft 15 is on the first gear 25 Dental pump 3 transferred, which in turn that with him meshing second gear drives. It is known in Way fuel through the suction hole 33 from the storage tank sucked into the suction space of the gear pump 3, the Gear pump 3 is also able to suck air in and out promote so that they are in empty fuel lines can vent independently.
- a certain minimum level of negative pressure is above that Spring constant of the pressure element 109 and the effective surfaces of the Control piston chamber 94 can be determined. This can, for example are around 700 millibars and can be large enough Represent negative pressure in the brake booster.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Rotary Pumps (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
- Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
- Valves And Accessory Devices For Braking Systems (AREA)
Description
- Fig. 1
- einen Schnitt durch die erfindungsgemäße Fördereinrichtung und
- Fig. 2
- eine Seitenansicht der Fig. 1 mit dem verdeckten Verlauf der Pumpkammer, der Zahnradpumpe und der Kraftstoffkanäle.
- 1
- Pumpengehäuse
- 3
- Zahnradpumpe
- 5
- Flügelzellenpumpe
- 7
- Pumpkammer
- 11
- Gehäusesteg
- 13
- Durchgangsbohrung
- 15
- Antriebswelle
- 17
- Mitnehmerscheibe
- 19
- Paßfeder
- 21
- Stirnfläche
- 23
- Pumpkammer
- 25
- erstes Zahnrad
- 27
- Stift
- 29
- Ansaugraum
- 31
- Druckraum
- 33
- Saugbohrung
- 35
- Druckkanal
- 37
- Steg
- 39
- Rücklaufkanal
- 41
- Verbindungsbohrung
- 43
- Gehäusedeckel
- 45
- Druckbohrung
- 47
- Rücklaufbohrung
- 49
- Wellendichtringe
- 51
- Rotor
- 52
- Koppeleinrichtung
- 53
- Innenwandfläche
- 55
- Kupplungsscheibe
- 56
- Gehäusedeckel
- 57
- Lagermittel
- 59
- Schlitz
- 61
- Flügel
- 64
- Außenwandfläche d. Rotors
- 65
- Ansaugbereich
- 67
- Anschlußbohrung
- 69
- Anschlußstutzen
- 71
- Rückschlagventil
- 91
- Steuerkolben
- 92
- Mitnehmerelemente
- 93
- Stirnfläche
- 94
- Steuerkolbenraum
- 96
- Axialbohrung
- 97
- Querbohrung
- 98
- Ringnut
- 101
- erste Bohrung
- 102
- zweite Bohrung
- 103
- Stirnfläche
- 104
- Belastungsmittel
- 106
- Bohrung
- 107
- Ringbund
- 109
- Steuerkolbensitz
Claims (13)
- Einrichtung zum Fördern von Kraftstoff aus einem Vorratstank zu einer Brennkraftmaschine eines Kraftfahrzeuges, mit einer in einer Förderleitung vom Vorratstank zur Brennkraftmaschine eingesetzten Förderpumpe (3), die in ihrem Gehäuse (1) wenigstens eine Pumpkammer (23) aufweist, mit rotierend angetriebenen Verdrängungselementen, insbesondere einer Zahnradpumpe, die Kraftstoff aus einem mit dem Vorratstank verbindbaren Ansaugraum (29) in einen wenigstens mittelbar mit der Brennkraftmaschine verbindbaren Druckraum (31) fördert, wobei die Förderpumpe (3) mit einer Luft fördernden Pumpe (5) eine Baueinheit bildet, wobei die Saugseite (65) der Luft fördernden Pumpe zur Erzeugung eines Unterdrucks mit einem Bremskraftverstärker des Kraftfahrzeuges verbunden ist, dadurch gekennzeichnet, daß zwischen der Förderpumpe (3) und der Luft fördernden Pumpe (5) eine Koppeleinrichtung (52) vorgesehen ist, die in Abhängigkeit des zu erzeugenden Unterdrucks die Luft fördernde Pumpe (5) von der Förderpumpe (3) trennt.
- Einrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Förderpumpe (3) von einer Antriebswelle (15) rotierend angetrieben ist und die Koppelvorrichtung (52) an einem zur Antriebswelle abgewandten Ende der Antriebswelle (15) angeordnet ist, die an der Luft fördernden Pumpe (5) angreift.
- Einrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß eine von der Saugseite zur Erzeugung eines Unterdrucks zur Koppelvorrichtung (52) führende Bohrung (96, 97, 99, 101, 102) vorgesehen ist, die die Koppeleinrichtung (52) ansteuert.
- Einrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Koppeleinrichtung (52) als Rutschkupplung ausgebildet ist, die einen axial zur Antriebswelle (15) bewegbaren Steuerkolben (91) aufweist, der an einer Kupplungsscheibe (55) der Luft fördernden Pumpe (5) angreift.
- Einrichtung nach Anspruch 4, dadurch gekennzeichnet, daß der Steuerkolben (91) einen mit Unterdruck beaufschlagbaren Steuerkolbenraum (94) aufweist, in dem ein gegen den Unterdruck arbeitendes Belastungsmittel (104) angeordnet ist, das sich gegenüber der Antriebswelle (15) abstützt.
- Einrichtung nach einem der Ansprüche 2 bis 5, dadurch gekennzeichnet, daß die Antriebswelle (15) eine mit der Bohrung (101, 102) in Verbindung stehende Ringnut (98) aufweist, von der wenigstens eine Radialbohrung (97) abzweigt und in eine zum Steuerkolbenraum (94) führende Axialbohrung (96) übergeht.
- Einrichtung nach einem der Ansprüche 4 bis 6, dadurch gekennzeichnet, daß der Steuerkolben (91) in einem in dem Gehäusesteg (11) angeordneten Steuerkolbensitz (109) axial bewegbar angeordnet ist.
- Einrichtung nach einem der Ansprüche 4 bis 7, dadurch gekennzeichnet, daß das zum Steuerkolben (91) weisende Ende der Antriebswelle (15) an dem Steuerkolben (91) angreifende Mitnehmerelemente (92) aufweist.
- Einrichtung nach einem der Ansprüche 4 bis 8, dadurch gekennzeichnet, daß die auf die Kupplungsscheibe (55) der Luft fördernden Pumpe (5) wirkende Axialkraft von einem an einem Gehäusedeckel (56) gelagerten Lagermittel (57) abgestützt ist.
- Einrichtung nach einem der Ansprüche 3 bis 9, dadurch gekennzeichnet, daß das zur Saugseite weisende Ende der Durchgangsbohrung (101) in Saugrichtung gesehen vor einem in den Ansaugraum führenden und ein Rückschlagventil (71) aufweisenden Anschlußstutzen (69) mündet.
- Einrichtung nach einem der Ansprüche 4 bis 10, dadurch gekennzeichnet, daß die Differenz der den Steuerkolben (91) beaufschlagenden Druckkraft des Belastungsmittels (104) und die aufbringbare Unterdruckkraft den Einsatzbeginn der Pumpe (5) bestimmt.
- Einrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Koppeleinrichtung (52) als elektrisch betätigbare Kupplung ausgebildet ist.
- Einrichtung nach Anspruch 1, dadurch gekennzeichnet, daß die Koppeleinrichtung (52) als magnetisch betätigbare Kupplung ausgebildet ist.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE19647053A DE19647053C1 (de) | 1996-11-14 | 1996-11-14 | Einrichtung zum Fördern von Kraftstoff aus einem Vorratstank zu einer Brennkraftmaschine eines Kraftfahrzeuges |
DE19647053 | 1996-11-14 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0843096A1 EP0843096A1 (de) | 1998-05-20 |
EP0843096B1 true EP0843096B1 (de) | 2002-12-04 |
Family
ID=7811643
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP97115817A Expired - Lifetime EP0843096B1 (de) | 1996-11-14 | 1997-09-11 | Koppeleinrichtung zwischen einer Kraftstoff-Förderpumpe und einer Luft fördernden Pumpe in einem Gehäuse angeordnet |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP0843096B1 (de) |
JP (1) | JPH10141165A (de) |
DE (2) | DE19647053C1 (de) |
Families Citing this family (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19956520A1 (de) * | 1999-11-24 | 2001-06-13 | Bosch Gmbh Robert | Vorrichtung zur Reduzierung der Axialkraftbelastung einer ein Fluid fördernden Pumpe |
EP2559903A1 (de) * | 2011-08-17 | 2013-02-20 | Wabco Automotive UK Limited | Verbesserte Vakuumpumpe |
Family Cites Families (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE2833167A1 (de) * | 1978-07-28 | 1980-02-14 | Barmag Barmer Maschf | Baueinheit, bestehend aus einer oelpumpe zur oelumlaufschmierung einer brennkraftmaschine und einer vakuumpumpe zur erzeugung eines vakuums fuer die bremskraftverstaerkung in kraftfahrzeugen |
SE7808719L (sv) * | 1978-08-17 | 1980-02-18 | Albin Motor Ab | Tryckmediepaverkad friktionskoppling for sammankoppling av tva i varandra inforbara maskinelement eller liknande, exempelvis ett hjul pa en axel, for vridmomentoverforing mellan dessa |
JPS6261868A (ja) * | 1985-09-10 | 1987-03-18 | Toyota Motor Corp | 電動式負圧ポンプの駆動制御装置 |
DE3637229C2 (de) * | 1985-11-13 | 1998-04-16 | Barmag Barmer Maschf | Baueinheit aus einer Hydraulikpumpe und einer Vakuumpumpe |
DE4317645C2 (de) * | 1993-05-27 | 1997-02-20 | Iav Motor Gmbh | Regelbare Zahnradpumpe |
US5370511A (en) * | 1993-12-27 | 1994-12-06 | Ford Motor Company | Clutch apparatus for a rotary compressor |
DE19513822C2 (de) * | 1995-04-12 | 1999-10-28 | Volkswagen Ag | Einrichtung zum Fördern von Kraftstoff aus einem Vorratstank zu einer Brennkraftmaschine eines Kraftfahrzeuges |
-
1996
- 1996-11-14 DE DE19647053A patent/DE19647053C1/de not_active Expired - Fee Related
-
1997
- 1997-09-11 DE DE59708881T patent/DE59708881D1/de not_active Expired - Fee Related
- 1997-09-11 EP EP97115817A patent/EP0843096B1/de not_active Expired - Lifetime
- 1997-11-12 JP JP9310107A patent/JPH10141165A/ja active Pending
Also Published As
Publication number | Publication date |
---|---|
DE59708881D1 (de) | 2003-01-16 |
DE19647053C1 (de) | 1998-04-30 |
EP0843096A1 (de) | 1998-05-20 |
JPH10141165A (ja) | 1998-05-26 |
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