EP0843096B1 - Coupling device for connecting a fuel pump and a vacuum pump having the same casing - Google Patents

Coupling device for connecting a fuel pump and a vacuum pump having the same casing Download PDF

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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
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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
Application number
EP97115817A
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German (de)
French (fr)
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EP0843096A1 (en
Inventor
Stanislaw Bodzak
Hanspeter Mayer
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP0843096A1 publication Critical patent/EP0843096A1/en
Application granted granted Critical
Publication of EP0843096B1 publication Critical patent/EP0843096B1/en
Anticipated expiration legal-status Critical
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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.

Description

Stand der TechnikState of the art

Die Erfindung geht von einer Einrichtung zum Fördern von Kraftstoff aus einem Vorratstank zu einer Brennkraftmaschine eines Kraftfahrzeuges nach der Gattung des Patentanspruchs 1 aus.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.

Aus der DE 195 13 822 A1 ist eine derartige Einrichtung bekannt geworden, die aus einer von der Brennkraftmaschine angetriebenen Förderpumpe gebildet ist, die Kraftstoff aus einem Vorratstank ansaugt und zur Brennkraftmaschine bzw. einer an dieser vorgesehenen Hochdruckeinspritzpumpe fördert. Die Förderpumpe weist in ihrem Gehäuse wenigstens eine Pumpkammer auf, in der ein Paar rotierend angetriebener und miteinander kämmender Zahnräder angeordnet ist, die Kraftstoff aus einem mit dem Vorratstank verbindbaren Ansaugraum entlang einem zwischen der Stirnfläche der Zahnräder und der Wand gebildeten Förderkanal in einen wenigstens mittelbar mit der Brennkraftmaschine verbindbaren Druckraum fördern. Für eine Verringerung des Bauraumes und des Fertigungsaufwandes ist im Gehäuse der Förderpumpe eine weitere, Luft fördernde Pumpe angeordnet, deren Saugseite mit einem Bremskraftverstärker des Kraftfahrzeuges verbunden ist. 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. For a reduction in installation space and the manufacturing effort is in the housing of the feed pump another, air-promoting pump arranged, the suction side with a brake booster of the motor vehicle is connected.

Die Förderpumpe und die Luft fördernde Pumpe sind koaxial nebeneinander in einem gemeinsamen Gehäuse angeordnet und werden von einer gemeinsamen Antriebswelle rotierend angetrieben. Die in das gemeinsame Gehäuse der Förderpumpe eingesetzte Luft fördernde Pumpe ist vorzugsweise als Flügelzellenpumpe ausgebildet. Die vorzugsweise als Zahnradpumpe ausgebildete Förderpumpe ist axial hintereinander zu der Flügelzellenpumpe angeordnet, so daß ein getriebenes Zahnrad der Förderpumpe und ein Rotor der Flügelzellenpumpe von der gemeinsamen Antriebswelle rotierend angetrieben werden. Dafür ist an einem das einem Koppelglied zur Nockenwelle abgewandten Ende der Antriebswelle eine Kupplungsscheibe aufgepreßt, die formschlüssig mit dem Rotor der Flügelzellenpumpe verbunden ist. Durch diese Anordnung wird während des Betriebs der Einrichtung zum Fördern von Kraftstoff durch die gemeinsame Antriebswelle sowohl die Förderpumpe als auch die Flügelzellenpumpe bzw. Unterdruckpumpe fortwährend angetrieben.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. For this is the one coupling link one end facing away from the camshaft Clutch disc pressed on, which is form-fitting with the rotor the vane pump is connected. By this arrangement is used during the operation of the device for conveying Fuel through both the common drive shaft Feed pump as well as the vane pump or Vacuum pump continuously driven.

Diese bekannte Einrichtung weist jedoch den Nachteil auf, daß aufgrund des Antriebes mit einer einzigen gemeinsamen Antriebswelle, die drehfest mit der Zahnrad- als auch Flügelzellenpumpe verbunden ist, ein zwangsweiser Antrieb beider Pumpen erfolgt. Dadurch wird im Bremskraftverstärker fortwährend ein Unterdruck erzeugt, der jedoch nur sporadisch, beispielsweise beim Bremsen mittels Bremskraftverstärker, erforderlich ist. Die fortwährend mitlaufende Unterdruck-Flügelzellenpumpe ist dadurch einem erhöhten Verschleiß der Flügel am Gehäuse der Unterdruckpumpe ausgesetzt. Darüber hinaus wird durch den zwangsweisen Antrieb der Flügelzellenpumpe eine erhöhte Antriebsleistung von der die Förderpumpe antreibenden Nockenwelle und somit der Brennkraftmaschine erforderlich. However, this known device has the disadvantage that due to the drive with a single common Drive shaft that rotates with the gear as well Vane pump is connected to a positive drive both pumps. This will result in the brake booster continuously creates a negative pressure, but it only sporadically, for example when braking using Brake booster is required. The continually the concurrent vacuum vane pump is one increased wear on the wings on the housing of the vacuum pump exposed. It is also forced by the Vane pump drive increased drive power from the camshaft driving the feed pump and thus the internal combustion engine required.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Einrichtung zum Fördern von Kraftstoff aus einem Vorratstank zu einer Brennkraftmaschine eines Kraftfahrzeuges mit den kennzeichnenden Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, daß durch die zwischen der Förderpumpe und der Luft fördernden Pumpe angeordnete Koppeleinrichtung eine bedarfsmäßige Ansteuerung der die Luft fördernde Pumpe erfolgen kann. Dadurch wird durch die nicht dauerhaft mitangetriebene Luft fördernde Pumpe eine Verringerung der Antriebsleistung erzielt. Darüber hinaus weist die erfindungsgemäße Einrichtung den Vorteil auf, daß durch die bedarfsangepaßte Betätigung der Luft fördernden Pumpe eine Verringerung des Verschleißes bei den Bauteilkomponenten der Luft fördernden Pumpe ermöglicht ist.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.

Dabei ist besonders vorteilhaft, daß durch die Koppeleinrichtung gewährleistet werden kann, daß ein Mindestwert an Unterdruck in dem Bremskraftverstärker vorliegt, der unmittelbar nach einem Bremsvorgang, bei dem der Unterdruck abnimmt, durch das Einschalten der Luft fördernden Pumpe wieder auf den erforderlichen Unterdruck im Bremskraftverstärker erhöht werden kann. Diese in Abhängigkeit von einem bestimmten Mindestwert an Unterdruck arbeitende Koppeleinrichtung wirkt sich insbesondere bei längeren Überlandfahrten oder Autobahnfahrten ohne einen Bremsvorgang vorteilhaft aus.It is particularly advantageous that 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.

Durch die vorteilhafte Anordnung der Koppeleinrichtung an der Antriebswelle kann die durch die axial hintereinander angeordnete Förderpumpe und Luft fördernde Pumpe erzielte Minimierung des Bauraumes aufrecht erhalten werden. Zudem kann auf eine Vielzahl der bereits vorhandenen Bauteilkomponenten von einer derartigen Einrichtung zum Fördern von Kraftstoff aus einem Vorratstank zu einer Brennkraftmaschine eines Fahrzeuges zurückgegriffen werden, bei der die Förderpumpe und die Luft fördernde Pumpe in einem gemeinsamen Pumpengehäuse als eine Baueinheit angeordnet sind.Due to the advantageous arrangement of the coupling device on the 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.

Nach einer vorteilhaften Ausgestaltung der Erfindung ist vorgesehen, daß an der die der Förderpumpe rotierend antreibenden Antriebswelle die Koppelvorrichtung vorgesehen ist. Dadurch kann ein geringer Bauraum der Einrichtung aufrecht erhalten werden. Desweiteren ist ein einfacher Antrieb der Koppeleinrichtung möglich, um die Drehbewegung auf die Flügelzellenpumpe zu übertragen.According to an advantageous embodiment of the invention provided that 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.

Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung ist vorgesehen, daß die Koppeleinrichtung unmittelbar mit der zum Bremskraftverstärker weisenden Saugseite über eine zur Koppeleinrichtung führende Durchgangsbohrung verbunden ist. Dadurch kann auf einfache Weise über den tatsächlich vorliegenden Unterdruck eine Ansteuerung der Koppeleinrichtung gegeben sein. Somit kann ohne Verwendung von zusätzlichen Bauteilen eine Ansteuerung der Koppeleinrichtung vorgesehen sein, die bei Erreichen eines vorgegebenen Unterdrucks die kraftschlüssige Verbindung zwischen der Förderpumpe und der Luft fördernden Pumpe trennt.According to a further advantageous embodiment of the invention it is provided that 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.

Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung ist vorgesehen, daß die Koppeleinrichtung als Rutschkupplung ausgebildet ist, die einen axial zur Antriebswelle bewegbaren Steuerkolben aufweist, der an einer Kupplungsscheibe der Luft fördernden Pumpe angreift. Durch die Ausgestaltung als Rutschkupplung kann in Abhängigkeit des Reibwertes der verwendeten Materialien der aufeinander wirkenden Oberflächen des Steuerkolbens und der Kupplungsscheibe eine exakte Auslegung der Rutschkupplung erfolgen. Desweiteren kann in Abhängigkeit des Mindestwertes an Unterdruck die kraftschlüssige Verbindung reproduzierbar getrennt werden. According to a further advantageous embodiment of the invention it is provided that 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. By designing as Slip clutch can depend on the coefficient of friction of the used materials of the interacting surfaces of the control piston and the clutch disc an exact The slip clutch is designed. Furthermore, in Dependence of the minimum value on negative pressure non-positive connection can be separated reproducibly.

Alternativ kann ebenso vorteilhaft vorgesehen sein, daß die Koppeleinrichtung als magnetisch oder hydraulisch oder elektrisch ansteuerbare Kupplung ausgebildet ist, die die entsprechenden Steuerbefehle über Sensoren erhält, die wiederum den aktuellen Unterdruck im Bremskraftverstärker erfassen können.Alternatively, it can also be advantageously provided that 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.

Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung ist vorgesehen, daß der Steuerkolben der Kopplungseinrichtung einen mit Unterdruck beaufschlagbaren Kolbenraum aufweist, in dem ein gegen den Unterdruck arbeitendes Belastungsmittel angeordnet ist. Das Belastungsmittel, das vorzugsweise als Druckfederelement ausgebildet ist, kann in Abhängigkeit der auf den Steuerkolbenraum wirkenden Axialkräfte des Unterdruckes angepaßt sein, so daß ab einem Mindestwert an Unterdruck die Federkraft überwunden werden kann, wodurch der Steuerkolben gegenüber der Kupplungsscheibe der Luft fördernden Pumpe getrennt werden kann. Dadurch kann eine Selbstregelung erzielt werden, bei der erst ab einem vorgegebenen Mindestwert an Unterdruck die Luft fördernde Pumpe abgeschalten wird.According to a further advantageous embodiment of the invention it is provided that the 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.

Desweiteren ist vorteilhaft, daß die von der Saugseite zur Antriebswelle führende Durchgangsbohrung in eine in der Antriebswelle angeordnete Ringnut übergeht, die mit einer Querbohrung in Verbindung steht und in eine zum Steuerkolben führende Axialbohrung führt. Dadurch kann in konstruktiv einfacher Weise der tatsächlich vorliegende Unterdruck der Saugseite auf den Steuerkolben einwirken.Furthermore, it is advantageous that the from the suction side to Drive shaft leading through hole in a in the Drive shaft arranged annular groove merges with a Cross bore is connected and in one to the control piston leading axial bore leads. This can be constructive simply the actual negative pressure of the Act on the suction side of the control piston.

Desweiteren ist vorteilhafterweise vorgesehen, daß die zur Saugseite führende Durchgangsbohrung in Saugrichtung gesehen vor einem in den Ansaugraum führenden und ein Rückschlagventil aufweisenden Anschlußstutzen mündet. Dadurch kann eine gezielte und exakte Ansteuerung der Koppeleinrichtung erzielt werden, die den tatsächlichen im Bremskraftverstärker herrschenden Unterdruck erfaßt.Furthermore, it is advantageously provided that 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.

Nach einer weiteren vorteilhaften Ausgestaltung der Erfindung ist vorgesehen, daß zwischen dem zum Steuerkolben weisenden Ende der Antriebswelle und dem Steuerkolben vorzugsweise klauenförmige Mitnehmerelemente vorgesehen sind. Dadurch kann der rotierende Antrieb der Koppeleinrichtung sichergestellt sein, wobei gleichzeitig eine axiale Bewegbarkeit des Steuerkolbens gegeben sein kann, um die Funktion des Auskoppelns und Einkoppelns aufrecht erhalten zu können.According to a further advantageous embodiment of the invention it is provided that between the one facing the control piston End of the drive shaft and the control piston preferably claw-shaped driver elements are provided. This can the rotating drive of the coupling device is ensured be, at the same time an axial mobility of the Control piston can be given to the function of the To be able to maintain coupling and coupling.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung, der Zeichnung und den Patentansprüchen entnehmbar.Further advantages and advantageous configurations of the The invention relates to the description of Drawing and the claims can be found.

Zeichnungdrawing

Ein Ausführungsbeispiel der erfindungsgemäßen Einrichtung zum Fördern von Kraftstoff aus einem Vorratstank zu einer Brennkraftmaschine eines Kraftfahrzeuges ist in der Zeichnung dargestellt und wird im folgenden näher erläutert. Es zeigen:

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.
An embodiment of the device according to the invention for delivering fuel from a storage tank to an internal combustion engine of a motor vehicle is shown in the drawing and is explained in more detail below. Show it:
Fig. 1
a section through the conveyor device according to the invention and
Fig. 2
a side view of Fig. 1 with the hidden course of the pump chamber, the gear pump and the fuel channels.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Die in den Figuren 1 und 2 nur mit ihren erfindungswesentlichen Bauteilen dargestellte Einrichtung zum Fördern von Kraftstoff aus einem nicht dargestellten Vorratsbehälter zu einer ebenfalls nicht näher dargestellten Brennkraftmaschine eines Kraftfahrzeuges, bzw. zu deren Hochdruckeinspritzpumpe, weist ein Pumpengehäuse 1 auf, in das eine als Zahnradpumpe 3 ausgebildete Kraftstoff-Förderpumpe und eine als Flügelzellenpumpe 5 ausgebildete, Luft fördernde Pumpe (im folgenden Unterdruckpumpe) eingesetzt sind.Those in Figures 1 and 2 only with their Essential components shown device for Pumping fuel from a not shown Storage container to a likewise not shown Internal combustion engine of a motor vehicle, or to their High-pressure injection pump, has a pump housing 1, in the one designed as a gear pump 3 fuel delivery pump and a vane pump 5, Air pump (hereinafter referred to as a vacuum pump) are used.

Dabei kann die Förderpumpe alternativ auch als eine andere Verdrängerpumpe, z.B. als Rollenzellenpumpe, ausgebildet sein. Das Pumpengehäuse 1 weist in seinem Inneren eine kreisförmige Ausnehmung auf, die eine zu einer Stirnfläche 9 des Pumpengehäuses 1 offene Pumpkammer 7 der Flügelzellenpumpe 5 bildet und die radial einwärts durch einen exzentrisch zur Pumpkammer 7 angeordneten zylindrischen Gehäusesteg 11 begrenzt ist. In diesem Gehäusesteg 11 ist eine axiale Durchgangsbohrung 13 eingebracht, in der eine Antriebswelle 15 drehbar geführt ist, die in der von der Stirnfläche 9 abgewandten Richtung aus dem Pumpengehäuse 1 ragt. Auf das aus dem Pumpengehäuse 1 ragende freie Ende der Antriebswelle 15 ist eine Mitnehmerscheibe 17 aufgepreßt, in der Nuten zur Aufnahme eines elastischen Koppelgliedes in Form einer Paßfeder 19 vorgesehen sind. Die von der Mitnehmerscheibe 17 vorstehenden Enden der Paßfeder 19 greifen formschlüssig in entsprechende Ausnehmungen einer nicht dargestellten Nockenwelle der Brennkraftmaschine, deren freies Wellenende zur Antriebswelle 15 fluchtend angeordnet ist, so daß die Drehbewegung der Antriebswelle über das elastische Koppelglied 19 auf die Mitnehmerscheibe 17 und auf die Antriebswelle 15 übertragen wird.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. 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 of the Drive plate 17 protruding ends of the parallel key 19th engage positively in corresponding recesses Not shown camshaft of the internal combustion engine, the Free shaft end aligned with the drive shaft 15 is, so that the rotational movement of the drive shaft on the elastic coupling member 19 on the drive plate 17 and on the drive shaft 15 is transmitted.

Das Pumpengehäuse 1 weist an seiner zweiten der Mitnehmerscheibe zugewandten Stirnfläche 21 eine ovale, eine Pumpkammer der Zahnradpumpe 3 bildende Ausnehmung auf, die durch eine Gehäuszwischenwand von der Pumpkammer getrennt ist und die von der Antriebswelle 15 durchdrungen wird. Dabei ist ein erstes Zahnrad 25 eines miteinander an seinen Stirnflächenen kämmenden Zahnradpaares auf der Antriebswelle 15 innerhalb der Pumpkammer 23 mittels eines in die Antriebswelle 15 eingepreßten Stiftes 27 formschlüssig mit dieser verbunden. Das zweite nicht näher dargestellte Zahnrad ist schräg zum ersten Zahnrad 25 versetzt angeordnet, wobei dessen Achse ebenfalls im Pumpengehäuse 1 gelagert ist. Ein oberer, sich radial an die Zahnräder in Höhe des Zahneingriffs anschließender Abschnitt der Pumpenkammer 23 bildet dabei einen Ansaugraum 29 und ein unterer, diesem am Zahnradeingriff gegenüberliegenden Abschnitt der Pumpkammer 23 einen Druckraum 31 der Zahnradpumpe 3. In den Ansaugraum 29 mündet eine Saugbohrung im Pumpengehäuse 1, die mit einer Kraftstoffleitung vom Vorratstank verbunden ist. Vom Druckraum 31 führt ein Druckkanal 25 ab, der durch eine Sicke in der Stirnfläche 21 des Pumpengehäuses 1 gebildet ist und der sich bis in einen Steg 37 des Pumpengehäuses 1 erstreckt. Parallel zu diesem Druckkanal 35 ist ein ebenfalls durch eine Sicke gebildeter Rücklaufkanal 39 angeordnet, der über eine Verbindungsbohrung 41 mit dem Druckkanal 35 verbunden ist und sich von dieser ausgehend etwa bis an das Ende des Druckkanales 35 erstreckt. Die Pumpkammer 23, der Druckkanal 35 und der Rücklaufkanal 39 sind auf der dem Gehäuse 1 abgewandten Seite durch einen auf der Stirnfläche 21 des Pumpengehäuses 1 dichtend aufgeschraubten ersten Gehäusedeckel 43 verschlossen, in dem eine vom Druckkanal 35 abführende Druckbohrung 45 und eine vom Rücklaufkanal 39 abführende Rücklaufbohrung 47 angeordnet sind. Dabei ist der Gehäusedeckel 43 seinerseits so an den Zylinderkopf der zu versorgenden Brennkraftmaschine angeflanscht, daß die Druckbohrung 45 und die Rücklaufbohrung 47 direkt an entsprechenden Kraftstoffkanälen im Zylinderkopf münden. Um die Pumpkammer 23 der Zahnradpumpe 3 gegen die Brennkraftmaschine und die Flügelzellenpumpe 5 abzudichten, sind neben verschiedenen Dichtringen am Gehäusedeckel zwei Wellendichtringe 49 auf der Antriebswelle 15 angeordnet, die die Pumpkammer 23 an der Antriebswelle 15 verschließen.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. In the suction chamber 29 opens a suction hole in the pump housing 1, which with a Fuel line from the storage tank is connected. from 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. Here is 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. Around the pump chamber 23 of the gear pump 3 against the To seal the internal combustion engine and the vane pump 5, are two different sealing rings on the housing cover Shaft seals 49 arranged on the drive shaft 15, the close the pump chamber 23 on the drive shaft 15.

Die in den Figuren 1 und 2 näher dargestellte Flügelzellenpumpe 5 wird aus einem in der Pumpkammer 7 angeordneten zylindrischen Rotor 51 mit einer axialen Bohrung gebildet, der mit seiner zylindrischen Innenwandfläche 53 in Form einer Gleitlagerung auf der Mantelfläche des zylindrischen Gehäusestegs 11 geführt ist. Der Rotor 51 ist über eine auf das der Zahnradpumpe abgewandte Ende der Antriebswelle 15 angeordnete Koppeleinrichtung 52 mit einer Kupplungsscheibe 55 verbunden, die sich andererseits an einem zweiten, die Pumpkammer 7 der Flügelzellenpumpe 5 verschließenden Gehäusedeckel 56 über ein Lagermittel 57 abstützt, der dichtend an der Stirnfläche 9 des Pumpengehäuses 1 verschraubt ist. In der die Pumpkammer 7 radial einwärts begrenzenden zylindrischen Außenwandfläche 64 des Rotors 51 sind vorzugsweise drei Schlitze 59 zur verschiebbaren Aufnahme von Flügeln vorgesehen, die in Drehrichtung des Rotors 51 auf dessen Radialebene gekippt sind. Da der Rotor 51 derart exzentrisch in der Pumpe 7 angeordnet ist, daß er zum Teil mit seiner Außenwandfläche 64 an der radialen Pumpenkammerwand 63 der Pumpkammer 7 anliegt, sind die Schlitze 59 so ausgeführt, daß sie ein vollständiges Eintauchen der Flügel 61 sowie eine ausreichende Führung bei maximalem Austauchen ermöglichen, sowie Dichtflächen zu den Flügeln 61 bilden, um bei einer Druckbeaufschlagung der im Rotor 51 befindlichen Flügelenden durch das Schmieröl die Flügel 61 zwangsweise während der Saugphase radial nach außen zu drücken und somit die Anpreßkraft und Dichtwirkung der Flügel 61 am Gehäuse 1 vor allem bei niedrigen Drehzahlen zu verbessern.The shown in Figures 1 and 2 in more detail 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. In which 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.

Ein oberer Bereich der Pumpkammer 7 bildet bei Drehung des Rotors 51 entgegen dem Uhrzeigersinn einen Ansaugbereich 65 der Flügelzellenpumpe 5, der in eine Anschlußbohrung 67 mündet, in die ein Anschlußstutzen 69 eingesetzt ist, auf den eine Schlauchleitung von einem Bremskraftverstärker des Kraftfahrzeuges aufsteckbar ist. Um dabei möglichst wirksam einen Unterdruck im Bremskraftverstärker aufbauen zu können, ist dem Anschlußstutzen 69 ein in Richtung Pumpkammer 7 öffnendes Rückschlagventil 71 oberhalb der Bohrung 67 vorgeschaltet.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. To be as effective as possible to be able to build up a vacuum in the brake booster, is the connecting piece 69 in the direction of the pump chamber 7 opening check valve 71 above bore 67 upstream.

Die Zahnradpumpe 3 und Flügelzellenpumpe 5 ist über die Koppeleinrichtung 52 antriebsverbunden, die von einer Antriebswelle 15 aufgenommen ist. Die Koppeleinrichtung 52 ist als Rutschkupplung ausgebildet, die in Abhängigkeit eines Mindestwerts an Unterdruck im Bremskraftverstärker eine kraftschlüssige Verbindung der Zahnradpumpe 3 zur Flügelzellenpumpe 5 trennt. Die Koppeleinrichtung 52 weist einen Steuerkolben 91 auf, der in einem Steuerkolbensitz 109 geführt ist und der von an der Antriebswelle 15 angeordneten Mitnehmerelementen 92 rotierend angetrieben ist. Der Steuerkolben 91 ist gleichzeitig über die Mitnehmerelemente 92 zur Antriebswelle 15 axial bewegbar gelagert, so daß eine zur Kupplungsscheibe 55 weisende Stirnfläche 93 an der Kupplungsscheibe 55 kraftschlüssig angreifen kann. Der Steuerkolben 91 und die Kupplungsscheibe 55 sind aus wärmebeständigem Material ausgebildet, das darüber hinaus verschleißarm ist. Die Stirnfläche 93 weist eine hohe Bearbeitungsgenauigkeit auf, so daß mit einer komplementären Fläche der Kupplungsscheibe 55 eine Rutschkupplung mit schnellem Eingriff und hoher Kraftübertragung gegeben ist.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.

Der Steuerkolben 91 weist einen Steuerkolbenraum 94 auf, der als zylindrische Sackbohrung ausgebildet ist. Der Steuerkolbenraum 94 steht mit einer in der Antriebswelle 15 ausgebildeten Axialbohrung 96 in Verbindung, die in eine Querbohrung 97 übergeht und in eine Ringnut 98 mündet. Eine von dem Anschlußstutzen 69 der Saugseite abzweigende erste Bohrung 101, die in eine zweite Bohrung 102 übergeht, mündet in die Ringnut 98 ein. Die Bohrungen 101 und 102 erstrecken sich bis zu einer Stirnfläche 103, die von einem ersten Gehäusedeckel 43 verschlossen ist. Diese Durchgangsbohrungen 101, 102 schließen einen Winkel von im wesentlichen 90° zueinander ein, wodurch eine einfache Herstellung der Bohrungen im Pumpengehäuse 1 gegeben ist. Über diese Durchgangsbohrungen 101 und 102 sowie der Ringnut 98, der zumindest einen Querbohrung 97 und der Axialbohrung 96 steht der Steuerkolbenraum 94 unmittelbar mit einem Unterdruckraum des Bremskraftverstärkers in Verbindung.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. A first branching from the connecting piece 69 of the suction side Bore 101, which merges into a second bore 102, opens into the 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. About these Through bores 101 and 102 and the annular groove 98, 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.

Die Kupplungsscheibe 55 ist über ein als Kugel ausgebildetes Lagermittel 57 zum zweiten Gehäusedeckel 56 angeordnet, wodurch die über die Koppeleinrichtung 52 wirkenden axialen Kräfte, die in eine Rotationsbewegung der Kupplungsscheibe 55 übertragen werden, unter Belastung reibungsarm aufgenommen werden.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.

Die Mitnehmerelemente 92 sind klauenförmig, als Paß-Federprofil oder als Keilwellenprofil ausgebildet und greifen in einen ebenso ausgebildeten Endbereich des Steuerkolbens 91 ein, der zur Antriebswelle 15 weist. In dem Steuerkolbenraum 94 ist ein Belastungsmittel 104 angeordnet, das als Druckfederelement ausgebildet ist. Das Belastungsmittel 104 stützt sich in einer Bohrung 106 der Antriebswelle 15 ab, damit eine Axialkraft auf den Steuerkolben 91 ausgeübt werden kann, der mit seiner Stirnfläche 93 an der Kupplungsscheibe 55 angreift. Die Antriebswelle 15 weist koaxial zu der Bohrung 106 einen Ringbund 107 auf, an dem die Mitnehmerelemente 92 angeordnet sind. Gleichzeitig stützt sich dieser Ringbund den Mitnehmerelementen gegenüberliegend an dem Steuerkolbensitz 109 des Gehäusesteges 11 ab. Der Steuerkolbensitz ist durch Feinbearbeitung, vorzugsweise Reiben, hergestellt. Der Steuerkolben 91 ist abdichtend mit seiner Mantelfläche zum Steuerkolbensitz 109 ausgebildet. Alternativ kann vorgesehen sein, daß der Steuerkolben einen Dichtring oder dergleichen aufweist, um eine abdichtende Anordnung zu ermöglichen.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. In the control piston room 94, 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.

Die erfindungsgemäße Fördereinrichtung arbeitet in folgender Weise. Während des Betriebes der Brennkraftmaschine treibt die Antriebswelle der Brennkraftmaschine die Antriebswelle 15 der Fördereinrichtung über die elastische Kupplung an der Mitnehmerscheibe 17 rotierend an. Diese Drehbewegung der Antriebswelle 15 wird auf das erste Zahnrad 25 der Zahnförderpumpe 3 übertragen, das seinerseits das mit ihm kämmende zweite Zahnrad antreibt. Dabei wird in bekannter Weise Kraftstoff über die Saugbohrung 33 aus dem Vorratstank in den Saugraum der Zahnradpumpe 3 angesaugt, wobei die Zahnradpumpe 3 auch in der Lage ist, Luft anzusaugen und zu fördern, so daß sie sich bei entleerten Kraftstoffleitungen selbständig entlüften kann. Dieser Kraftstoff wird dann zwischen den kämmenden Stirnflächen der Zahnräder im Druckraum gefördert, wovon der Kraftstoff über einen Druckkanal zur Druckbohrung und weiter zur Brennkraftmaschine oder einer an dieser vorgesehenen Hochdruckeinspritzpumpe strömt. Der über die Kupplungseinrichtung 52 rotierend angetriebene Rotor 51 der Flügelzellenpumpe 5 saugt während seines Umlaufes in der Pumpkammer 7 über den Anschlußstutzen 69 Luft vom Bremskraftverstärker ab, wozu das durch die Flügel 61 begrenzte Volumen der einzelnen Kammer 11 während der Drehbewegung des Rotors 51 von der Mündung der Anschlußbohrung 67 ausgehend vergrößert wird, so daß in bekannter Weise ein Unterdruck erzeugt wird. Im weiteren Verlauf der Drehbewegung, nach Austauchen der jeweiligen Kammer aus der Überdeckung mit der Anschlußbohrung 67 verringert sich deren Volumen, so daß das eingeschlossene Luftvolumen gemeinsam mit dem die Druckkammer 7 durchströmenden Schmiermittel mit Druck in eine Abführungsbohrung gefördert wird, von der dieses Gemisch wieder dem Schmiermittelkreislauf der Brennkraftmaschine zugeführt wird. Dabei vermeidet das Rückschlagventil 71 ein Rückströmen von Luft zum Bremskraftverstärker, insbesondere nach dem Abschalten der Brennkraftmaschine, so daß der erzeugte Unterdruck aufrecht erhalten werden kann.The conveyor device according to the invention 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. That fuel will then between the meshing end faces of the gears in the Pressure chamber promoted, of which the fuel over a Pressure channel to the pressure bore and on to the internal combustion engine or a high-pressure injection pump provided on this flows. The rotating via the coupling device 52 driven rotor 51 of the vane pump 5 sucks during its circulation in the pump chamber 7 via the connecting piece 69 Air from the brake booster, which is through the Wing 61 limited volume of each chamber 11 during the rotational movement of the rotor 51 from the mouth of the Port bore 67 is enlarged starting, so that in known vacuum is generated. In the further Course of the rotary movement, after the respective one has emerged Chamber from overlap with connection hole 67 their volume decreases so that the trapped Air volume together with the pressure chamber 7 flowing lubricant with pressure into a Drain hole is promoted by this mixture again the lubricant circuit of the internal combustion engine is fed. The check valve 71 thereby avoids Backflow of air to the brake booster, in particular after switching off the internal combustion engine, so that the generated negative pressure can be maintained.

Ein bestimmter Mindestwert an Unterdruck ist über die Federkonstante des Druckelementes 109 und die Wirkflächen des Steuerkolbenraums 94 bestimmbar. Dieser kann beispielsweise bei 700 Millibar liegen und kann einen genügend großen Unterdruck in dem Bremskraftverstärker darstellen.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.

Aufgrund der von dem Anschlußstutzen 69 abzweigenden Durchgangsbohrungen 101 und 102, die in die Ringnut 98, die Querbohrung 97 und Axialbohrung 69 der Antriebswelle 15 übergehen und in den Steuerkolbenraum 94 münden, liegt in diesem Steuerkolbenraum 94 der tatsächlich herrschende Unterdruck an. Sobald dieser Mindestwert an Unterdruck erreicht wird, erfolgt eine Trennung der kraftschlüssigen Verbindung zwischen der Stirnfläche 93 des Steuerkolbens 91 zu der Kupplungsscheibe 55. Dabei arbeitet der Unterdruck entgegen der Druckkraft des Belastungsmittels 104, wodurch der Steuerkolben 91 entgegen der Druckkraft des Belastungsmittels 104 bewegt werden kann. Durch das Rückschlagventil 71 und die Wellendichtung an der Antriebswelle 15 und des Steuerkolbensitzes 109 kann der Unterdruck aufrecht erhalten bleiben. Dadurch wird nur die Förderpumpe 3 angetrieben, während die Flügelzellenpumpe 5 stillsteht.Because of the branching from the connecting piece 69 Through holes 101 and 102 in the annular groove 98, the Cross bore 97 and axial bore 69 of drive shaft 15 pass over and open into the control piston chamber 94 lies in this control piston chamber 94 the actually prevailing Negative pressure. As soon as this minimum value of negative pressure is reached, the non-positive is separated Connection between the end face 93 of the control piston 91 to the clutch disc 55. The vacuum works against the pressure force of the loading means 104, whereby the control piston 91 against the pressure force of the Loading means 104 can be moved. By the Check valve 71 and the shaft seal on the Drive shaft 15 and the piston seat 109 can Maintain negative pressure. This will only make the Feed pump 3 driven while the vane pump 5 stationary.

Sobald der Unterdruck in dem Bremskraftverstärker, beispielsweise durch einen Bremsvorgang oder Undichtheiten, einen gewissen Mindestwert unterschreitet, bewirkt das Belastungsmittel 104 aufgrund des abfallenden Unterdrucks, daß der Steuerkolben 91 wieder zur Kupplungsscheibe 55 gepreßt wird. Dadurch kann eine Mitnahme der Kupplungsscheibe 55 und somit ein Antreiben der Flügelzellenpumpe 5 erfolgen, um den erforderlichen Unterdruck im Bremskraftverstärker wieder aufzubauen. Durch die geringe Luft- und Ölleckage am Steuerkolbensitz 109, der in dem Gehäusesteg 11 vorgesehen ist, wird der im Steuerkolbenraum 94 anliegende Unterdruck langsam abgebaut, so daß die Stirnfläche 93 des Steuerkolbens 91 langsam eine kraftschlüssige Verbindung zur Kupplungsscheibe 55 aufbaut, wodurch ein gleichmäßiges Hochlaufen der Flügelzellenpumpe 5 bewirkt werden kann.As soon as the vacuum in the brake booster, for example due to braking or leaks, falls below a certain minimum value Loading means 104 due to the falling negative pressure, that the control piston 91 back to the clutch disc 55th is pressed. This can entrain the clutch disc 55 and thus driving the vane pump 5, the required vacuum in the brake booster rebuild. Due to the low air and oil leakage on the Control piston seat 109, which is provided in the housing web 11 is, the negative pressure present in the control piston chamber 94 slowly degraded so that the face 93 of the control piston 91 slowly a positive connection to the Clutch disc 55 builds up, creating a uniform Startup of the vane pump 5 can be effected.

Durch dieses bedarfsmäßige Zuschalten der Flügelzellenpumpe 5 während des Kraftstoff-Förderbetriebes kann eine Verringerung des Verschleißes der Flügelzellenpumpe 5 erzielt werden, wodurch ebenso eine Verringerung der Antriebsleistung erforderlich ist. Es ist somit mit der erfindungsgemäßen Einrichtung möglich, die in konstruktiv einfacher Weise in einem gemeinsamen Gehäuse vorgesehene Anordnung der Aggregate zum Fördern von Kraftstoff und zum Aufbau des Unterdrucks mit einem erheblich reduzierten Bauraum aufrecht zu erhalten und eine Verringerung der Antriebsleistung der Brennkraftmaschine über die Antriebswelle und eine Verringerung des Verschleißes der Flügelzellenpumpe 5 zu erzielen. By switching on the vane pump 5 as required during fuel delivery, a reduction may occur the wear of the vane pump 5 can be achieved, thereby also reducing the drive power is required. It is thus with the invention Setup possible in a structurally simple manner a common housing arrangement of the units to deliver fuel and build up the vacuum with maintain a significantly reduced installation space and a reduction in the drive power of the internal combustion engine via the drive shaft and a reduction in wear to achieve the vane pump 5.

BezugszahlenlisteLIST OF REFERENCE NUMBERS

11
Pumpengehäusepump housing
33
Zahnradpumpegear pump
55
FlügelzellenpumpeVane pump
77
Pumpkammerpumping chamber
1111
Gehäusesteghousing web
1313
DurchgangsbohrungThrough Hole
1515
Antriebswelledrive shaft
1717
Mitnehmerscheibedriver disc
1919
Paßfederadjusting spring
2121
Stirnflächeface
2323
Pumpkammerpumping chamber
2525
erstes Zahnradfirst gear
2727
Stiftpen
2929
Ansaugraumsuction
3131
Druckraumpressure chamber
3333
Saugbohrungsuction bore
3535
Druckkanalpressure channel
3737
Stegweb
3939
RücklaufkanalReturn channel
4141
Verbindungsbohrungconnecting bore
4343
Gehäusedeckelhousing cover
4545
Druckbohrungpressure bore
4747
RücklaufbohrungReturn bore
4949
WellendichtringeShaft seals
5151
Rotorrotor
5252
Koppeleinrichtungcoupling device
5353
InnenwandflächeInner wall surface
5555
Kupplungsscheibeclutch disc
5656
Gehäusedeckelhousing cover
5757
Lagermittelbearing means
5959
Schlitzslot
6161
Flügelwing
6464
Außenwandfläche d. RotorsOuter wall surface d. rotor
6565
Ansaugbereichsuction
6767
Anschlußbohrungconnecting bore
6969
Anschlußstutzenconnecting branch
7171
Rückschlagventilcheck valve
9191
Steuerkolbenspool
9292
Mitnehmerelementeentrainment
9393
Stirnflächeface
9494
SteuerkolbenraumControl piston chamber
9696
Axialbohrungaxial bore
9797
Querbohrungcross hole
9898
Ringnutring groove
101101
erste Bohrungfirst hole
102102
zweite Bohrungsecond hole
103103
Stirnflächeface
104104
Belastungsmittelloading means
106106
Bohrungdrilling
107107
Ringbundcollar
109109
SteuerkolbensitzControl piston seat

Claims (13)

  1. Device for delivering fuel from a storage tank to an internal combustion engine of a motor vehicle, having a delivery pump (3), which is fitted in a delivery line leading from the storage tank to the internal combustion engine and has in its housing (1) at least one pump chamber (23), with displacement elements which are driven in rotation, in particular a gear pump which delivers fuel out of an induction chamber (29), which can be connected to the storage tank, into a compression chamber (31), which can be at least indirectly connected to the internal combustion engine, the delivery pump (3) forming a structural unit with a pump (5) which delivers air, the suction side (65) of the air-delivering pump being connected to a brake booster of the motor vehicle in order to generate a reduced pressure, characterized in that a coupling device (52) is provided between the delivery pump (3) and the air-delivering pump (5), which coupling device disconnects the air-delivering pump (5) from the delivery pump (3) as a function of the reduced pressure which is to be generated.
  2. Device according to Claim 1, characterized in that the delivery pump (3) is driven in rotation by a drive shaft (15), and the coupling device (52) is arranged at an end, which is remote from the drive shaft, of the drive shaft (15) which acts on the air-delivering pump (5).
  3. Device according to Claim 1 or 2, characterized in that there is a bore (96, 97, 99, 101, 102) which leads from the suction side to the coupling device (52) in order to generate a reduced pressure and which actuates the coupling device (52).
  4. Device according to one of the preceding claims, characterized in that the coupling device (52) is designed as a slipping clutch which has a control piston (91), which can move axially with respect to the drive shaft (15) and acts on a clutch disc (55) of the air-delivering pump (5).
  5. Device according to Claim 4, characterized in that the control piston (91) has a control-piston chamber (94) to which a reduced pressure can be applied and in which there is arranged a loading means (104) which operates against the reduced pressure and is supported with respect to the drive shaft (15).
  6. Device according to one of Claims 2 to 5, characterized in that the drive shaft (15) has an annular groove (98) which is in communication with the bore (101, 102) and from which at least one radial bore (97) branches off and merges into an axial bore (96) leading to the control-piston chamber (94).
  7. Device according to one of Claims 4 to 6, characterized in that the control piston (91) is arranged in an axially moveable manner in a control-piston seat (109) arranged in the housing web (11).
  8. Device according to one of Claims 4 to 7, characterized in that that end of the drive shaft (15) which faces towards the control piston (91) has driver elements (92) which engage on the control piston (91).
  9. Device according to one of Claims 4 to 8, characterized in that the axial force which acts on the clutch disc (55) of the air-delivering pump (5) is supported by a bearing means (57) mounted on a housing cover (56).
  10. Device according to one of Claims 3 to 9, characterized in that that end of the through-bore (101) which faces towards the suction side opens out upstream, as seen in the suction direction, of a connection stub (69) which leads into the induction chamber and has a nonreturn valve (71).
  11. Device according to one of Claims 4 to 10, characterized in that the difference between the pressure force of the loading means (104) acting on the control piston (91) and the reduced-pressure force which can be applied determines the start of use of the pump (5).
  12. Device according to Claim 1, characterized in that the coupling device (52) is designed as an electrically actuable clutch.
  13. Device according to Claim 1, characterized in that the coupling device (52) is designed as a magnetically actuable clutch.
EP97115817A 1996-11-14 1997-09-11 Coupling device for connecting a fuel pump and a vacuum pump having the same casing Expired - Lifetime EP0843096B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19647053A DE19647053C1 (en) 1996-11-14 1996-11-14 Device for delivering fuel from a storage tank to an internal combustion engine of a motor vehicle
DE19647053 1996-11-14

Publications (2)

Publication Number Publication Date
EP0843096A1 EP0843096A1 (en) 1998-05-20
EP0843096B1 true EP0843096B1 (en) 2002-12-04

Family

ID=7811643

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97115817A Expired - Lifetime EP0843096B1 (en) 1996-11-14 1997-09-11 Coupling device for connecting a fuel pump and a vacuum pump having the same casing

Country Status (3)

Country Link
EP (1) EP0843096B1 (en)
JP (1) JPH10141165A (en)
DE (2) DE19647053C1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19956520A1 (en) * 1999-11-24 2001-06-13 Bosch Gmbh Robert Device for reducing the axial force load of a pump delivering a fluid
EP2559903A1 (en) 2011-08-17 2013-02-20 Wabco Automotive UK Limited Improved vacuum pump

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2833167A1 (en) * 1978-07-28 1980-02-14 Barmag Barmer Maschf CONSTRUCTION UNIT CONSTRUCTING AN OIL PUMP FOR LUBRICATING OIL CIRCUIT FOR AN INTERNAL COMBUSTION ENGINE AND A VACUUM PUMP FOR GENERATING A VACUUM FOR THE BRAKE POWER REINFORCEMENT IN MOTOR VEHICLES
SE7808719L (en) * 1978-08-17 1980-02-18 Albin Motor Ab PRINTED MEDICINE FRICTION COUPLING FOR COUPLING TWO IN EACH OTHER INFORMABLE MACHINE ELEMENTS OR SIMILAR, FOR EXAMPLE A WHEEL ON A SHAFT, FOR TORQUE TRANSMISSION BETWEEN THESE
JPS6261868A (en) * 1985-09-10 1987-03-18 Toyota Motor Corp Drive controller for motor negative pressure pump
DE3637229C2 (en) * 1985-11-13 1998-04-16 Barmag Barmer Maschf Unit consisting of a hydraulic pump and a vacuum pump
DE4317645C2 (en) * 1993-05-27 1997-02-20 Iav Motor Gmbh Adjustable gear pump
US5370511A (en) * 1993-12-27 1994-12-06 Ford Motor Company Clutch apparatus for a rotary compressor
DE19513822C2 (en) * 1995-04-12 1999-10-28 Volkswagen Ag Device for delivering fuel from a storage tank to an internal combustion engine of a motor vehicle

Also Published As

Publication number Publication date
DE59708881D1 (en) 2003-01-16
JPH10141165A (en) 1998-05-26
DE19647053C1 (en) 1998-04-30
EP0843096A1 (en) 1998-05-20

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