EP2271839B1 - Low pressure pump - Google Patents

Low pressure pump Download PDF

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Publication number
EP2271839B1
EP2271839B1 EP09725577.2A EP09725577A EP2271839B1 EP 2271839 B1 EP2271839 B1 EP 2271839B1 EP 09725577 A EP09725577 A EP 09725577A EP 2271839 B1 EP2271839 B1 EP 2271839B1
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EP
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Prior art keywords
pump
power
parts
shut
rotary piston
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EP09725577.2A
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German (de)
French (fr)
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EP2271839A2 (en
Inventor
Felix Arnold
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Robert Bosch GmbH
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Robert Bosch GmbH
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/48—Rotary-piston pumps with non-parallel axes of movement of co-operating members
    • F04C18/54—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees
    • F04C18/56—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/565—Rotary-piston pumps with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing the axes of cooperating members being on the same plane
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • 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
    • F04C23/008—Hermetic 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
    • F04C2220/00—Application
    • F04C2220/10—Vacuum

Definitions

  • the invention relates to a rotary pump for gaseous media according to the preamble of the main claim.
  • a known rotary lobe pump of the generic type US Pat. DE 42 41 320 C2
  • the teeth of each co-interacting with the cycloidal part cooperating part have corresponding tooth crests, which run along the flanks of the cycloid part, wherein the tooth combs have a freely configurable radius.
  • a high degree of tightness is achieved between the toothed ridges of the shut-off part and the flanks of the cycloidal part, which is of considerable importance especially when used as a low-pressure pump or vacuum pump.
  • Zykloidenteil having pump to provide the power unit and shut-off each double, is already available in this known pump and also the ability to connect the two, however, the same size work spaces together.
  • the invention has for its object to develop a rotary piston pump for gaseous media of the type mentioned, which has the advantages of the mentioned in the generic state of the art pump, but in addition, especially for large series, is low to produce, with a relatively large pressure range can be covered , In particular, to achieve a correspondingly lower pressure (vacuum), and this using two synchronized workspaces.
  • the description and the claims are based on an absolute pressure of 0, in contrast, the atmospheric pressure 1 bar with vacuum designation between absolute pressure 0 and atmospheric pressure about 1 bar corresponding to 1000 millibars.
  • the rotary piston pump according to the invention with the characterizing features of the main claim has the advantage that it is a 2-stage pump is, in which the first power section is driven by the rotating part of the electric motor, with which it is firmly connected, while the non-co-rotating part of the electric motor is anchored in the motor housing, and wherein the second power section is taken over a clutch from the first power section and co-rotated accordingly.
  • the two power units are rotatably mounted via radial bearings in a conventional manner in the housing and according to the invention, in particular in the motor housing of the electric motor.
  • the two power parts are pressed with their frontally arranged tooth combs on those of the corresponding Absperrteils, which, in particular by the rounding of the tooth combs, a desired form-fit arises, because of its tightness, especially when used for gaseous media of particular importance is.
  • the motor armature and magnet set of the electric motor receiving Motor housing on both ends by the respective Absperrteil and power unit receiving pump housing closed which also not only extremely cheap production and assembly allows, but above all, greatly simplified future service.
  • the first pump with its first, directly driven by the electric motor power unit a greater volumetric power than the driven at the same speed second pump with the second power part, wherein by series connection of the pump a total of 2 stages Pump is created.
  • the pump outlet of the second pump is connected to the atmosphere and its inlet to the outlet of the first pump.
  • the outlet and inlet of the first and second pumps are connected to each other via the annular space formed in the electric motor between coil and armature.
  • the rotary lobe pump serves as a vacuum pump for a brake booster of a service brake system of a motor vehicle, wherein a line connection in the corresponding pump housing for a line to the brake booster is present at the inlet of the first pump.
  • a brake booster the executed by the driver's foot on the brake pedal force is amplified in a known manner, without causing a sensitive grading of the braking force is impaired.
  • an extra vacuum pump was used in diesel engines for actuating the brake booster, wherein the assist force is proportional to the driver's foot force. It is significant that very low pressures of about 100 millibars can be achieved by the invention.
  • a rotatable magnet set 3 is arranged in a cylindrically shaped motor housing 1, wherein this magnet set is rotatably mounted to the motor housing 1 through ball bearings 4.
  • the housing 5 and 6 of individual pumps 9 and 10 close, with part-spherical interior spaces, said pump housing 5 and 6 screwed onto the end faces of the motor housing 1 and O-ring seals 7 outside the housing 1, 5, 6 are sealed.
  • the axes of the part-spherical interiors of the individual pumps fall into the axis of the electric motor.
  • To fasten the pump housing 5, 6 on the electric motor housing 1 serve screws 8, which allow a quick disassembly.
  • the two arranged in the pump housings 5 and 6 individual pumps 9 and 10 have a different volume performance, namely, the volume capacity of the first pump 9 is greater than that of the second pump 10.
  • Both pumps 9 and 10 have the same displacement system, as by The above-mentioned prior art is known. These are in each case a power unit 11, which is driven by the electric motor, of somewhat larger volume power and 12, on the other hand, of somewhat smaller volume power and in each case a shut-off part 13 of somewhat greater volume power and a somewhat smaller volume power.
  • the shut-off parts 13 and 14 are rotatably mounted on ball bearings 15 in the pump housings 5 and 6.
  • the power parts 11 and 12 are arranged coaxially with the electric motor, whereas the shut-off parts 13 and 14 are mounted at a certain angle to this axis of rotation to thereby to achieve the required volume change of the pump work spaces during rotation, namely an increase or decrease during rotation and wherein the axes of rotation of these shut-off parts intersect with the axis of the power parts or of the electric motor.
  • the basic function of this type of rotary engine is the DE 42 41 320 C2 removable.
  • Fig. 1 For the sake of simplicity, the present application has shown the two associated pumps in a position in which that working space normally present between the power unit and the shut-off member is not recognizable according to the section plane selected there.
  • the power unit 11 is rotationally connected to the motor armature 2 and has a rotary coupling not shown in detail to turn the power unit 12 of the pump 10.
  • This may be a rotary joint of various kinds - it is decisive that it allows axial mobility to the magnet set, so that over a arranged between the power parts 11 and 12 coil spring 16, the two power parts are charged to their associated shut-off parts 13, 14 out , This axial load an improved form fit between flanks and tooth combs of the frontally opposite teeth is achieved.
  • the larger volume capacity of the first pump 9 is achieved in that the pumping parts, namely power part 11 and shut-off part 13, in the spherical region have a larger diameter than the corresponding parts 12 and 14 in the second pump 10 of smaller volume.
  • the pumping power with respect to the first pump 9 is greater than that of the downstream one due to the larger volume capacity second pump 10, which in turn is connected to the outlet side with the atmosphere and the inlet side with the outlet of the pump.
  • this second pump 10 has an outlet port 17 to the atmosphere.
  • the first pump is, as indicated by dash-dotted lines, inlet side with a in Fig. 3 connected vacuum brake booster of a motor vehicle.
  • the pump should produce at least 500 millibar for such a brake booster.
  • About such a vacuum brake booster foot power of the driver is reinforced.
  • the support force increases when the brake is applied proportional to the foot force up to the so-called control point. From here, the support force no longer increases.
  • the in Fig. 3 illustrated a prospectus removed brake booster is constructed as follows.
  • a diaphragm 19 separates a vacuum chamber 20 (actually a low pressure chamber) into which the first pump line 18 flows from a working chamber 21.
  • a piston rod 22 transmits the applied foot force to a working piston 23 while the increased braking force is applied to the push rod 24 acts on the master cylinder, not shown.
  • the vacuum chamber 20 and the working chamber 21 are connected to one another via channels in the valve housing. Via the line 18 there is a low pressure in both chambers.
  • the piston rod 22 moves toward the vacuum chamber 20 and presses the cuff of a double valve 25 against the valve seat.
  • vacuum chamber 20 and working chamber 21 are again connected to each other, so that there is the same pressure in both chambers.
  • the text of this section has been taken from the brochure of a manufacturer of such brake booster and is only used to explain the necessity and use of vacuum pumps).

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressors, Vaccum Pumps And Other Relevant Systems (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Drehkolbenpumpe für gasförmige Medien nach der Gattung des Hauptanspruchs. Bei einer bekannten Drehkolbenpumpe der gattungsgemäßen Art ( DE 42 41 320 C2 ) ist ein wesentliches Merkmal, dass "die Zähne des jeweils mit dem Zykloidenteil kämmend zusammenwirkenden Teils entsprechende Zahnkämme aufweisen, welche an den Flanken des Zykloidenteils entlang laufen, wobei die Zahnkämme einen frei gestaltbaren Radius aufweisen". Hierdurch wird bei deren Anwendung als Pumpe eine hohe Dichtheit zwischen den Zahnkämmen des Absperrteils und den Flanken des Zykloidenteils erzielt, was besonders beim Einsatz als Niederdruckpumpe oder Vakuumpumpe von erheblicher Bedeutung ist. Bei einer solchen ein Zykloidenteil aufweisenden Pumpe, das Leistungsteil und Absperrteil jeweils doppelt vorzusehen, ist bei dieser bekannten Pumpe bereits vorhanden und auch die Möglichkeit, die beiden dort allerdings gleichgroßen Arbeitsräume miteinander zu verbinden.The invention relates to a rotary pump for gaseous media according to the preamble of the main claim. In a known rotary lobe pump of the generic type (US Pat. DE 42 41 320 C2 ) is an essential feature that "the teeth of each co-interacting with the cycloidal part cooperating part have corresponding tooth crests, which run along the flanks of the cycloid part, wherein the tooth combs have a freely configurable radius." As a result, when used as a pump, a high degree of tightness is achieved between the toothed ridges of the shut-off part and the flanks of the cycloidal part, which is of considerable importance especially when used as a low-pressure pump or vacuum pump. In such a Zykloidenteil having pump to provide the power unit and shut-off each double, is already available in this known pump and also the ability to connect the two, however, the same size work spaces together.

Bekanntlich entsteht durch ein solches Verbinden der Arbeitsräume eine entsprechende Vergrößerung der jeweiligen Leistung, also der Pumpleistung, als wenn die Arbeitsräume nur eines Leistungsteils genutzt würden. Zwar würde durch eine solche Parallelschaltung die Förderleistung entsprechend vergrößert werden. Der Druck jedenfalls bliebe gleich, es sei denn, er wird nicht extra gesteuert. Nicht zuletzt ist die Mitnahme des zweiten Leistungsteils bei dieser bekannten Pumpe über einen gemeinsamen als Arbeitsteil dienenden Ring nicht unproblematisch, ganz abgesehen davon, dass die Herstellung einer solchen Pumpe, insbesondere wenn sie über einen Elektromotor angetrieben werden soll, aufwendig ist.As is known, such a connection of the work spaces results in a corresponding increase in the respective power, ie the pump power, as if the working spaces of only one power section were used. Although by such a Parallel circuit, the capacity can be increased accordingly. The pressure would remain the same, unless it is not controlled extra. Not least, the entrainment of the second power unit in this known pump via a common ring serving as a working part is not unproblematic, quite apart from the fact that the production of such a pump, especially if it is to be driven by an electric motor, is expensive.

Aus der US 3 817 666 A ist eine Drehkolbenpumpe mit zwei Rotorpaaren bekannt. Aus der WO 2007/128303 A1 ist eine Drehkolbenpumpe mit einem einzelnen Rotorpaar und mit einem integrierten Elektromotor bekannt.From the US Pat. No. 3,817,666 is a rotary pump with two pairs of rotors known. From the WO 2007/128303 A1 is known a rotary pump with a single rotor pair and with an integrated electric motor.

Zugrundeliegende AufgabeUnderlying task

Der Erfindung liegt die Aufgabe zugrunde eine Drehkolbenpumpe für gasförmige Medien der Eingangs genannten Art zu entwickeln, die die Vorteile der im gattungsgemäßen Stand der Technik erwähnten Pumpe aufweist, aber zusätzlich, insbesondere für Großserien, günstig herstellbar ist, mit der ein verhältnismäßig großer Druckbereich abdeckbar ist, insbesondere auch zur Erzielung eines entsprechend niedereren Druck (Vakuums), und dies unter Nutzung von zwei synchronisierten Arbeitsräumen. Die Beschreibung und die Ansprüche gehen von einem absoluten Druck 0 aus, demgegenüber der Atmosphärendruck 1 bar aufweist mit Vakuumbezeichnung zwischen absolutem Druck 0 und Atmosphärendruck ca. 1 bar entsprechend 1000 Millibar.The invention has for its object to develop a rotary piston pump for gaseous media of the type mentioned, which has the advantages of the mentioned in the generic state of the art pump, but in addition, especially for large series, is low to produce, with a relatively large pressure range can be covered , In particular, to achieve a correspondingly lower pressure (vacuum), and this using two synchronized workspaces. The description and the claims are based on an absolute pressure of 0, in contrast, the atmospheric pressure 1 bar with vacuum designation between absolute pressure 0 and atmospheric pressure about 1 bar corresponding to 1000 millibars.

Die Erfindung und ihre VorteileThe invention and its advantages

Die erfindungsgemäße Drehkolbenpumpe mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, dass es sich um eine 2-Stufen-Pumpe handelt, bei der das erste Leistungsteil durch den rotierenden Teil des Elektromotors, mit dem er fest verbunden ist, angetrieben wird, während der nicht mitrotierende Teil des Elektromotors im Motorgehäuse verankert ist, und wobei das zweite Leistungsteil über eine Kupplung vom ersten Leistungsteil mitgenommen wird und entsprechend mitrotiert. Hierbei sind die beiden Leistungsteile über Radiallager in üblicher Weise im Gehäuse und erfindungsgemäß insbesondere im Motorgehäuse des Elektromotors drehgelagert.The rotary piston pump according to the invention with the characterizing features of the main claim has the advantage that it is a 2-stage pump is, in which the first power section is driven by the rotating part of the electric motor, with which it is firmly connected, while the non-co-rotating part of the electric motor is anchored in the motor housing, and wherein the second power section is taken over a clutch from the first power section and co-rotated accordingly. Here, the two power units are rotatably mounted via radial bearings in a conventional manner in the housing and according to the invention, in particular in the motor housing of the electric motor.

Nach der Erfindung sind zwischen den Leistungsteilen, diese in Richtung Absperrteile hin belastende elastische Mittel angeordnet, wobei als elastische Mittel insbesondere eine mit den Leistungsteilen achsgleich angeordnete Schraubenfeder dient. Durch diese mitrotierenden elastischen Mittel werden die beiden Leistungsteile mit ihren stirnseitig angeordneten Zahnkämmen auf jene des entsprechenden Absperrteils gedrückt, wodurch, insbesondere durch die Abrundung der Zahnkämme, ein gewünschter Formschluss entsteht, der, seiner Dichtheit wegen, besonders beim Einsatz für gasförmige Medien von besonderer Bedeutung ist.According to the invention are arranged between the power parts, these in the direction of shut-off loading elastic means, in particular serves as an elastic means with the power parts arranged coaxially coil spring. By this co-rotating elastic means, the two power parts are pressed with their frontally arranged tooth combs on those of the corresponding Absperrteils, which, in particular by the rounding of the tooth combs, a desired form-fit arises, because of its tightness, especially when used for gaseous media of particular importance is.

Nach der Erfindung dient für einen Verdrehschluss zwischen den Leistungsteilen eine Steckkupplung, welche eine axiale Relativbewegung der Teile zulässt. Hierdurch bleibt einerseits die Wirkung der elastischen Mittel erhalten, es wird aber andererseits eine Kupplung ermöglicht mit geringem Herstell- und Montageaufwand.According to the invention is used for a Verdrehschluss between the power parts a plug-in coupling, which allows an axial relative movement of the parts. As a result, on the one hand the effect of the elastic means is retained, but on the other hand a coupling is made possible with low manufacturing and assembly costs.

Nach einer zusätzlichen Ausgestaltung der Erfindung ist das Motoranker und Magnetsatz des Elektromotors aufnehmende Motorgehäuse auf beiden Stirnseiten durch die jeweils Absperrteil und Leistungsteil aufnehmenden Pumpengehäuse verschließbar, was ebenfalls nicht nur eine äußerst günstige Herstellung und Montage ermöglicht, sondern vor allem auch einen zukünftigen Service stark vereinfacht.According to an additional embodiment of the invention, the motor armature and magnet set of the electric motor receiving Motor housing on both ends by the respective Absperrteil and power unit receiving pump housing closed, which also not only extremely cheap production and assembly allows, but above all, greatly simplified future service.

Nach einer zusätzlichen vorteilhaften Ausgestaltung der Erfindung weist die erste Pumpe mit ihrem ersten, vom Elektromotor unmittelbar angetriebene Leistungsteil, eine größere volumetrische Leistung auf, als die mit gleicher Drehzahl angetriebene zweite Pumpe mit deren zweiten Leistungsteil, wobei durch Hintereinanderschalten der Pumpen insgesamt eine 2-Stufen-Pumpe entsteht. Hierdurch ist beispielsweise bei der Verwendung als Pumpe niederen Drucks (Vakuumpumpe) der Pumpenauslass der zweiten Pumpe mit der Atmosphäre verbunden und deren Einlass mit dem Auslass der ersten Pumpe.According to an additional advantageous embodiment of the invention, the first pump with its first, directly driven by the electric motor power unit, a greater volumetric power than the driven at the same speed second pump with the second power part, wherein by series connection of the pump a total of 2 stages Pump is created. As a result, for example, when used as a low pressure pump (vacuum pump), the pump outlet of the second pump is connected to the atmosphere and its inlet to the outlet of the first pump.

Nach einer zusätzlichen Ausgestaltung der Erfindung sind Auslass und Einlass der ersten und zweiten Pumpe über den im Elektromotor zwischen Spule und Anker gebildeten Ringraum miteinander verbunden.According to an additional embodiment of the invention, the outlet and inlet of the first and second pumps are connected to each other via the annular space formed in the electric motor between coil and armature.

Nach einer die Anwendung der erfindungsgemäßen Drehkolbenpumpe betreffenden Ausgestaltung der Erfindung dient sie als Vakuumpumpe für einen Bremskraftverstärker einer Betriebsbremsanlage eines Kraftfahrzeuges, wobei zum Einlass der ersten Pumpe ein Leitungsanschluss im entsprechenden Pumpengehäuse für eine Leitung zum Bremskraftverstärker hin vorhanden ist. Über einen solchen Bremskraftverstärker wird in bekannter Weise die vom Fuß des Fahrers auf das Bremspedal ausgeführte Kraft verstärkt, ohne dass dabei ein feinfühliges Abstufen der Bremskraft beeinträchtigt wird. Während früher bei Otto-Motoren hierfür meist der Saugrohrdruck verwendet wurde, wurde bei Dieselmotoren zur Betätigung des Bremskraftverstärkers eine extra Vakuumpumpe eingesetzt, wobei die Unterstützungskraft proportional zur Fußkraft des Fahrers steht. Bezeichnend ist, dass durch die Erfindung sehr niedere Drücke von ca. 100 Millibar erzielbar sind.According to an embodiment of the invention relating to the application of the rotary lobe pump according to the invention, it serves as a vacuum pump for a brake booster of a service brake system of a motor vehicle, wherein a line connection in the corresponding pump housing for a line to the brake booster is present at the inlet of the first pump. About such a brake booster, the executed by the driver's foot on the brake pedal force is amplified in a known manner, without causing a sensitive grading of the braking force is impaired. While earlier at Otto engines for this mostly the intake manifold pressure was used, an extra vacuum pump was used in diesel engines for actuating the brake booster, wherein the assist force is proportional to the driver's foot force. It is significant that very low pressures of about 100 millibars can be achieved by the invention.

Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Beschreibung, der Zeichnung und den Ansprüchen entnehmbar.Further advantages and advantageous embodiments of the invention are the following description, the drawings and claims removed.

Zeichnungdrawing

Ein Ausführungsbeispiel des Gegenstandes der Erfindung ist in der Zeichnung dargestellt und im folgenden näher beschrieben.An embodiment of the object of the invention is illustrated in the drawing and described in more detail below.

Es zeigen:

Fig. 1
einen Längsschnitt durch eine erfindungsgemäße Drehkolbenpumpe;
Fig. 2
eine Ansicht der Drehkolbenpumpe aus Fig. 1 gemäß dem Pfeil I in Fig. 1 und
Fig. 3
einen bekannten Vakuumbremskraftverstärker im Längsschnitt aber anderem Maßstab, als mögliche Anwendung der Erfindung.
Show it:
Fig. 1
a longitudinal section through a rotary piston pump according to the invention;
Fig. 2
a view of the rotary lobe pump Fig. 1 in accordance with the arrow I in Fig. 1 and
Fig. 3
a known vacuum brake booster in longitudinal section but different scale, as a possible application of the invention.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Bei der in Fig. 1 dargestellten erfindungsgemäßen Drehkolbenpumpe ist in einem zylindrisch ausgebildeten Motorgehäuse 1 ein rotierbarer Magnetsatz 3 angeordnet, wobei dieser Magnetsatz zum Motorgehäuse 1 hin über Kugellager 4 verdrehbar gelagert ist. An die Stirnseiten des Motorgehäuses 1 schließen sich die Gehäuse 5 und 6 von Einzelpumpen 9 und 10 an, mit teilsphärischen Innenräumen, wobei diese Pumpengehäuse 5 und 6 auf die Stirnseiten des Motorgehäuses 1 geschraubt und über O-Ring Dichtungen 7 nach außerhalb der Gehäuse 1, 5, 6 abgedichtet sind. Die Achsen der teilsphärischen Innenräume der Einzelpumpen fallen in die Achse des Elektromotors. Zur Befestigung der Pumpengehäuse 5, 6 am Elektromotorgehäuse 1 dienen Schrauben 8, die eine schnelle Demontage ermöglichen. Die beiden in den Pumpengehäusen 5 und 6 angeordneten Einzelpumpen 9 und 10 weisen eine unterschiedliche Volumenleistung auf, und zwar ist die Volumenleistung der ersten Pumpe 9 größer als die der zweiten Pumpe 10. Beide Pumpen 9 und 10 weisen das gleiche Verdrängungssystem auf, wie es durch den eingangs genannten Stand der Technik bekannt ist. Es handelt sich jeweils um ein durch den Elektromotor angetriebenes Leistungsteil 11 etwas größerer Volumenleistung und 12 demgegenüber etwas kleinerer Volumenleistung und jeweils einem Absperrteil 13 etwas größerer Volumenleistung und 14 etwas kleinerer Volumenleistung. Die Absperrteile 13 und 14 sind auf Kugellagern 15 in den Pumpengehäusen 5 und 6 drehbar gelagert.At the in Fig. 1 illustrated rotary piston pump according to the invention a rotatable magnet set 3 is arranged in a cylindrically shaped motor housing 1, wherein this magnet set is rotatably mounted to the motor housing 1 through ball bearings 4. At the end faces of the motor housing 1, the housing 5 and 6 of individual pumps 9 and 10 close, with part-spherical interior spaces, said pump housing 5 and 6 screwed onto the end faces of the motor housing 1 and O-ring seals 7 outside the housing 1, 5, 6 are sealed. The axes of the part-spherical interiors of the individual pumps fall into the axis of the electric motor. To fasten the pump housing 5, 6 on the electric motor housing 1 serve screws 8, which allow a quick disassembly. The two arranged in the pump housings 5 and 6 individual pumps 9 and 10 have a different volume performance, namely, the volume capacity of the first pump 9 is greater than that of the second pump 10. Both pumps 9 and 10 have the same displacement system, as by The above-mentioned prior art is known. These are in each case a power unit 11, which is driven by the electric motor, of somewhat larger volume power and 12, on the other hand, of somewhat smaller volume power and in each case a shut-off part 13 of somewhat greater volume power and a somewhat smaller volume power. The shut-off parts 13 and 14 are rotatably mounted on ball bearings 15 in the pump housings 5 and 6.

Die Leistungsteile 11 und 12 sind achsgleich mit dem Elektromotor angeordnet, wohingegen die Absperrteile 13 und 14 unter einem bestimmten Winkel zu dieser Drehachse gelagert sind, um dadurch die erforderliche Volumenänderung der Pumpenarbeitsräume beim Rotieren zu erzielen, nämlich ein Zunehmen bzw. Abnehmen während des Rotierens und wobei sich die Drehachsen dieser Absperrteile mit der Achse der Leistungsteile bzw. des Elektromotors schneiden. Die grundsätzliche Funktion dieser Art von Drehkolbenmaschine ist der DE 42 41 320 C2 entnehmbar. In Fig. 1 der vorliegenden Anmeldung wurden der Einfachheithalber die beiden zugeordneten Pumpen in einer Stellung gezeigt, in der jener normalerweise zwischen Leistungsteil und Absperrteil vorhandene Arbeitsraum gemäß der dort gewählten Schnittebene nicht erkennbar ist. Jedenfalls ist das Leistungsteil 11 drehschlüssig mit dem Motoranker 2 verbunden und weist eine nicht näher dargestellte Drehkupplung auf, um das Leistungsteil 12 der Pumpe 10 mitzudrehen. Hierbei kann es sich um eine Drehkupplung unterschiedlichster Art handeln - maßgebend ist, dass sie eine axiale Beweglichkeit zum Magnetsatz zulässt, so dass über eine zwischen den Leistungsteilen 11 und 12 angeordnete Schraubenfeder 16 die beiden Leistungsteile zu den ihnen zugeordneten Absperrteilen 13, 14 hin belastet sind. Durch diese axiale Belastung wird ein verbesserter Formschluss zwischen Flanken und Zahnkämmen der stirnseitig einander gegenüberliegenden Zähne erreicht.The power parts 11 and 12 are arranged coaxially with the electric motor, whereas the shut-off parts 13 and 14 are mounted at a certain angle to this axis of rotation to thereby to achieve the required volume change of the pump work spaces during rotation, namely an increase or decrease during rotation and wherein the axes of rotation of these shut-off parts intersect with the axis of the power parts or of the electric motor. The basic function of this type of rotary engine is the DE 42 41 320 C2 removable. In Fig. 1 For the sake of simplicity, the present application has shown the two associated pumps in a position in which that working space normally present between the power unit and the shut-off member is not recognizable according to the section plane selected there. In any case, the power unit 11 is rotationally connected to the motor armature 2 and has a rotary coupling not shown in detail to turn the power unit 12 of the pump 10. This may be a rotary joint of various kinds - it is decisive that it allows axial mobility to the magnet set, so that over a arranged between the power parts 11 and 12 coil spring 16, the two power parts are charged to their associated shut-off parts 13, 14 out , This axial load an improved form fit between flanks and tooth combs of the frontally opposite teeth is achieved.

Die größere Volumenleistung der ersten Pumpe 9 wird dadurch erreicht, dass die pumpenden Teile, nämlich Leistungsteil 11 und Absperrteil 13, im sphärischen Bereich einen größeren Durchmesser aufweisen als die entsprechenden Teile 12 und 14 in der zweiten Pumpe 10 kleinerer Volumenleistung. Die Pumpleistung bezüglich der ersten Pumpe 9 ist aufgrund der größeren Volumenleistung größer als jene der nachgeschalteten zweiten Pumpe 10, die wiederum auslassseitig mit der Atmosphäre verbunden ist und einlassseitig mit dem Auslass der Pumpe 9.The larger volume capacity of the first pump 9 is achieved in that the pumping parts, namely power part 11 and shut-off part 13, in the spherical region have a larger diameter than the corresponding parts 12 and 14 in the second pump 10 of smaller volume. The pumping power with respect to the first pump 9 is greater than that of the downstream one due to the larger volume capacity second pump 10, which in turn is connected to the outlet side with the atmosphere and the inlet side with the outlet of the pump. 9

Wie in Fig. 2 dargestellt weist diese zweite Pumpe 10 einen Ausgangsanschluss 17 zur Atmosphäre auf. Die erste Pumpe ist, wie strichpunktiert angedeutet, einlassseitig mit einem in Fig. 3 dargestellten Vakuum-Bremskraftverstärker eines Kraftfahrzeugs verbunden. Die Pumpe sollte für einen solchen Bremskraftverstärker mindestens 500 Millibar erzeugen. Über einen solchen Vakuum-Bremskraftverstärker wird die Fußkraft des Fahrers verstärkt. Die Unterstützungskraft erhöht sich dabei beim Betätigen der Bremse proportional zur Fußkraft bis zum sogenannten Aussteuerpunkt. Von hier ab erhöht sich die Unterstützungskraft nicht mehr.As in Fig. 2 illustrated, this second pump 10 has an outlet port 17 to the atmosphere. The first pump is, as indicated by dash-dotted lines, inlet side with a in Fig. 3 connected vacuum brake booster of a motor vehicle. The pump should produce at least 500 millibar for such a brake booster. About such a vacuum brake booster foot power of the driver is reinforced. The support force increases when the brake is applied proportional to the foot force up to the so-called control point. From here, the support force no longer increases.

Der in Fig. 3 dargestellte einem Prospekt entnommenem Bremskraftverstärker ist wie folgt aufgebaut. Eine Membran 19 trennt eine Unterdruckkammer 20 (eigentlich eine Kammer niederem Drucks), in die die Leitung 18 der ersten Pumpe mündet, von einer Arbeitskammer 21. Eine Kolbenstange 22 überträgt die eingesteuerte Fußkraft auf einen Arbeitskolben 23, während die verstärkte Bremskraft auf die Druckstange 24 auf den nicht dargestellten Hauptbremszylinder wirkt. Bei nicht betätigter Bremse sind Unterdruckkammer 20 und Arbeitskammer 21 über Kanäle im Ventilgehäuse miteinander verbunden. Über die Leitung 18 herrscht ein niederer Druck in beiden Kammern. Sobald ein Bremsvorgang beginnt bewegt sich die Kolbenstange 22 zur Unterdruckkammer 20 hin und drückt die Manschette eines Doppelventils 25 gegen den Ventilsitz. Damit sind Unterdruckkammer 20 und Arbeitskammer 21 voneinander getrennt. Da bei weitergehender Bewegung der Kolbenstange 22 ein Reaktionskolben 26 von der Manschette des Doppelventils 25 abhebt, strömt atmosphärische Luft in die Arbeitskammer 21. Jetzt herrscht in der Arbeitskammer ein höherer Druck als in der Unterdruckkammer. Der Atmosphärendruck wirkt über die Membran 19 auf den Membranteller, an dem die Membran anliegt. Weil das Ventilgehäuse vom Membranteller in Richtung Unterdruckkammer 20 mitgeführt wird, führt dies zu einer Unterstützung der Fußkraft. Jetzt drücken Fußkraft und Unterstützungskraft den Membranteller gegen die Kraft der Druckfeder. Dadurch bewegt sich die Druckstange 24 und überträgt die Ausgangskraft zum Hauptbremszylinder. Nach Beendigung des Bremsvorgangs sind Unterdruckkammer 20 und Arbeitskammer 21 wieder miteinander verbunden, so dass in beiden Kammern der gleiche Druck herrscht. (Der Text dieses Abschnitts wurde dem Prospekt eines Herstellers solcher Bremskraftverstärker entnommen und dient lediglich zur Erläuterung der Notwendigkeit und dem Einsatz von Vakuumpumpen).The in Fig. 3 illustrated a prospectus removed brake booster is constructed as follows. A diaphragm 19 separates a vacuum chamber 20 (actually a low pressure chamber) into which the first pump line 18 flows from a working chamber 21. A piston rod 22 transmits the applied foot force to a working piston 23 while the increased braking force is applied to the push rod 24 acts on the master cylinder, not shown. When the brake is not actuated, the vacuum chamber 20 and the working chamber 21 are connected to one another via channels in the valve housing. Via the line 18 there is a low pressure in both chambers. Once a braking operation begins, the piston rod 22 moves toward the vacuum chamber 20 and presses the cuff of a double valve 25 against the valve seat. Thus, vacuum chamber 20 and working chamber 21 are separated from each other. As with further movement of the piston rod 22nd a reaction piston 26 lifts off from the cuff of the double valve 25, atmospheric air flows into the working chamber 21. Now there is a higher pressure in the working chamber than in the vacuum chamber. The atmospheric pressure acts via the diaphragm 19 on the diaphragm plate against which the diaphragm rests. Because the valve housing is carried by the diaphragm plate in the direction of the vacuum chamber 20, this leads to a support of the foot force. Now foot force and support force press the diaphragm plate against the force of the compression spring. As a result, the push rod 24 moves and transmits the output force to the master cylinder. After completion of the braking process vacuum chamber 20 and working chamber 21 are again connected to each other, so that there is the same pressure in both chambers. (The text of this section has been taken from the brochure of a manufacturer of such brake booster and is only used to explain the necessity and use of vacuum pumps).

Alle in der Beschreibung, den nachfolgenden Ansprüchen und der Zeichnung dargestellten Merkmale können sowohl einzeln als auch in beliebiger Kombination miteinander erfindungswesentlich sein.All in the description, the following claims and the drawings illustrated features may be essential to the invention both individually and in any combination.

BezugszahlenlisteLIST OF REFERENCE NUMBERS

11
Motorgehäusemotor housing
22
Motorankermotor armature
33
Magnetsatzset of magnets
44
Kugellagerball-bearing
55
Pumpengehäusepump housing
66
Pumpengehäusepump housing
77
O-RingeO-rings
88th
Schraubenscrew
99
Erste Pumpe (größerer Volumenleistung)First pump (larger volume capacity)
1010
Zweite Pumpe (kleinerer Volumenleistung)Second pump (smaller volume capacity)
1111
Leistungsteil von 9Power section of 9
1212
Leistungsteil von 10Power section of 10
1313
Absperrteil von 9Shut off part of 9
1414
Absperrteil von 10Shut off part of 10
1515
Lager von 13 und 14Stock of 13 and 14
1616
Schraubenfedercoil spring
1717
Ausgangsanschlussoutput port
1818
Leitungmanagement
1919
Membranmembrane
2020
UnterdruckkammerVacuum chamber
2121
Arbeitskammerworking chamber
2222
Kolbenstangepiston rod
2323
Arbeitskolbenworking piston
2424
Druckstangepushrod
2525
Doppelventildouble valve
2626
Reaktionskolbenreaction flask

Claims (7)

  1. Rotary piston pump for gaseous media
    - having an axially and radially mounted power part (11, 12) which is configured as a spur tooth ball segment and is connected to a drive apparatus (1, 2, 3),
    - having a shut-off part (13, 14) which is of identical radial seal diameter, is likewise configured as a spur tooth ball segment and is driven by the power part,
    - having working spaces between the parts, which working spaces are formed by way of meshing of the teeth of the power part (11, 12) and those of the shut-off part (13, 14),
    - the power part (11, 12) and the shut-off part (13, 14) being guided in a radially sealing manner in a pump housing (5, 6) and having a respectively different number of teeth on their end sides which interact with one another, in particular, in order to achieve a pumping action or in order to generate a low pressure,
    - having a linear positively locking connection, delimiting the working space, between flanks and tooth meshing of the interacting teeth which lie opposite one another,
    - the teeth of one of the interacting parts, the power part (11, 12) or the shut-off part (13, 14), having a cycloidal development of its running face as a cycloid part,
    - the teeth of the other part which interacts in a meshing manner in each case with the cycloid part having corresponding tooth meshing, the radius of which can be configured freely and which runs along the flanks of the cycloid part, and
    - the said pump (9, 10) which is formed from a power part (11, 12) and a shut-off part (13, 14) being present in each case in a double configuration, the said pumps (9, 10) being driven jointly and it being possible for their working spaces to be connected to one another, the power parts (11, 12) which are present in a double configuration being arranged coaxially on the drive side, characterized
    - in that a first power part (11) is driven by an electric motor (2, 3) which is likewise arranged coaxially in a motor housing (1) on the drive side, and
    - in that the second power part (12) is rotated jointly by the first power part (11) in a rotationally locking manner, and
    - elastic means (16) which load the power parts (11, 12) in the direction of shut-off elements (13, 14) are arranged between the said power parts (11, 12), and in that, in particular, a helical spring (16) which is arranged coaxially with the power parts (11, 12) serves as elastic means, and
    - a plug-in coupling which permits an axial relative movement of the parts (11, 12) serves to produce a rotationally locked connection between the power parts.
  2. Rotary piston pump according to Claim 1, characterized in that the motor housing (1) which accommodates the motor armature (2) and the magnet set (3) of the electric motor is of largely cylindrical configuration, it being possible for their end sides to be closed by the two pump housings (5, 6).
  3. Rotary piston pump according to one of the preceding claims, characterized in that the rotating parts (2, 11, 12, 13, 14) are arranged in pivot bearings (4, 15) in the housings.
  4. Rotary piston pump according to one of the preceding claims, characterized in that the first pump (9) in each case with its shut-off part (13) and first power part (11) has a greater volumetric performance than the second pump (10), driven at the same rotational speed, with the second power part (12).
  5. Rotary piston pump according to one of the preceding claims, characterized in that the annular space which is formed in the electric motor (1, 2, 3) between the magnet set (3) and the motor armature (2) or motor housing (1) serves as a connection to the respectively other pump (9, 10) or the outlet of the first pump and the inlet of the second pump.
  6. Rotary piston pump according to one of the preceding claims, characterized in that, from the inlet of the first pump (9), there is a connector (18) in the corresponding pump housing (5) for a line to a brake booster and, from the outlet of the second pump (10), there is a connector (17) to atmosphere.
  7. Use of the rotary piston pump according to one of the preceding claims as a vacuum pump for a brake booster of a motor vehicle.
EP09725577.2A 2008-03-28 2009-03-27 Low pressure pump Active EP2271839B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008016293A DE102008016293A1 (en) 2008-03-28 2008-03-28 Low pressure pump
PCT/DE2009/000394 WO2009117993A2 (en) 2008-03-28 2009-03-27 Low pressure pump

Publications (2)

Publication Number Publication Date
EP2271839A2 EP2271839A2 (en) 2011-01-12
EP2271839B1 true EP2271839B1 (en) 2015-10-28

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Application Number Title Priority Date Filing Date
EP09725577.2A Active EP2271839B1 (en) 2008-03-28 2009-03-27 Low pressure pump

Country Status (7)

Country Link
US (1) US9022752B2 (en)
EP (1) EP2271839B1 (en)
JP (1) JP5101731B2 (en)
CN (1) CN101981320B (en)
BR (1) BRPI0910111B1 (en)
DE (1) DE102008016293A1 (en)
WO (1) WO2009117993A2 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011087606A1 (en) * 2011-12-01 2013-06-06 Robert Bosch Gmbh Motor vehicle system device and method for operating a motor vehicle system device
DE102014209140A1 (en) * 2013-05-23 2014-11-27 Robert Bosch Gmbh delivery unit

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2674952A (en) * 1951-07-02 1954-04-13 Jacobsen Jacob Rotary pump or engine
CH449428A (en) * 1966-02-21 1967-12-31 Wildhaber Ernest Displacement machine
US3817666A (en) * 1973-02-12 1974-06-18 E Wildhaber Rotary positive displacement unit
DE4241320C2 (en) * 1991-12-09 2002-01-17 Arnold Felix Rotary engine
US6171076B1 (en) * 1998-06-10 2001-01-09 Tecumseh Products Company Hermetic compressor assembly having a suction chamber and twin axially disposed discharge chambers
US7044717B2 (en) * 2002-06-11 2006-05-16 Tecumseh Products Company Lubrication of a hermetic carbon dioxide compressor
US20040202557A1 (en) * 2003-02-09 2004-10-14 Shigeru Suzuki Electric pump
US20050254970A1 (en) * 2004-05-17 2005-11-17 James Mayer Quick connect pump to pump mount and drive arrangement
DE102006012481A1 (en) * 2005-03-16 2006-09-21 Cor Pumps + Compressors Ag Hydraulic pump designed as rotary piston machine combines casings of electric motor and pump, and includes driving and driven components in angular configuration with axial play
BRPI0709777B1 (en) * 2006-05-10 2019-06-25 Robert Bosch Gmbh ROTARY SWING MACHINE

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BRPI0910111B1 (en) 2019-10-29
JP2011515617A (en) 2011-05-19
BRPI0910111A2 (en) 2015-12-29
CN101981320B (en) 2014-01-22
EP2271839A2 (en) 2011-01-12
US9022752B2 (en) 2015-05-05
WO2009117993A3 (en) 2010-04-01
WO2009117993A2 (en) 2009-10-01
CN101981320A (en) 2011-02-23
US20110052438A1 (en) 2011-03-03
JP5101731B2 (en) 2012-12-19
DE102008016293A1 (en) 2009-10-01

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