EP2271839A2 - Low pressure pump - Google Patents

Low pressure pump

Info

Publication number
EP2271839A2
EP2271839A2 EP09725577A EP09725577A EP2271839A2 EP 2271839 A2 EP2271839 A2 EP 2271839A2 EP 09725577 A EP09725577 A EP 09725577A EP 09725577 A EP09725577 A EP 09725577A EP 2271839 A2 EP2271839 A2 EP 2271839A2
Authority
EP
European Patent Office
Prior art keywords
pump
power
parts
shut
rotary
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.)
Granted
Application number
EP09725577A
Other languages
German (de)
French (fr)
Other versions
EP2271839B1 (en
Inventor
Felix Arnold
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2271839A2 publication Critical patent/EP2271839A2/en
Application granted granted Critical
Publication of EP2271839B1 publication Critical patent/EP2271839B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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 (DE 42 41 320 C2) is an essential feature that "the teeth of each combing with the cycloidal part together acting part corresponding tooth combs which run along the planks of Zykloidenteils, the tooth combs a free
  • a high degree of tightness is achieved between the toothed ridges of the shut-off part and the flanks of the cycloid part, which is of considerable importance especially when used as a low-pressure pump or vacuum pump and to provide double shut-off in each case, is already present in this known pump and also the possibility to connect the two, however, the same size work spaces together.
  • the invention has the 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 lobe pump according to the invention with the characterizing features of the main claim has the advantage that it is a 2-stage Pum ⁇ e 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 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 one another via the annular space formed in the electric motor between coil and armature.
  • the invention 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 provided at the inlet of the first pump.
  • a line connection in the corresponding pump housing for a line to the brake booster is provided at the inlet of the first pump.
  • 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.
  • FIG. 1 shows a longitudinal section through a rotary piston pump according to the invention.
  • Fig. 2 is a view of the rotary piston pump of FIG. 1 according to the arrow I in Fig. 1 and
  • Fig. 3 shows a known vacuum brake booster in longitudinal section but other scale, as a possible application of the invention. Description of the embodiment
  • a rotatable magnet set 3 is arranged in a cylindrically shaped motor housing 1, said 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 DE 42 41 320 C2 removable.
  • Fig. 1 of the present application for the sake of simplicity, the two associated pumps have been shown in a position in which that normally between the power unit and Absperrteil existing working space according to the section plane selected there is not recognizable.
  • 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
  • 8th 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 output port 17 to the atmosphere.
  • the first pump is, as indicated by dash-dotted lines, on the inlet side connected to a vacuum brake booster of a motor vehicle shown in Fig. 3.
  • 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.
  • 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).

Landscapes

  • 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)

Abstract

The invention relates to a low pressure pump/vacuum pump for gaseous media, comprising two interacting combs the teeth of which are configured as cycloidal components, the duplicate compressor stages being interconnected. A power unit of the pumps/compressors is driven and the power unit of the other pump/compressor, which is arranged coaxially, is entrained via a rotational connection.

Description

COR pumps + compressors AG. 70173 Stuttgart COR pumps + compressors AG. 70173 Stuttgart
NiederdruckpumpeLow pressure pump
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 zusammen wirkenden Teils entsprechende Zahnkämme aufweisen, welche an den Planken 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 (DE 42 41 320 C2) is an essential feature that "the teeth of each combing with the cycloidal part together acting part corresponding tooth combs which run along the planks of Zykloidenteils, the tooth combs a free In this way, 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 cycloid part, which is of considerable importance especially when used as a low-pressure pump or vacuum pump and to provide double shut-off in each case, is already present in this known pump and also the possibility 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.
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 the 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-Pumρe 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 lobe pump according to the invention with the characterizing features of the main claim has the advantage that it is a 2-stage Pumρe 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 einer vorteilhaften Ausgestaltung 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 an advantageous embodiment of 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 einer zusätzlichen vorteilhaften Ausgestaltung 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 an additional advantageous embodiment of 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 zu sätzlichen 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 larger volumetric power than the driven at the same speed second pump with the second power part, wherein by connecting the pumps in series a total of 2 Stage 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 one another 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 one 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 provided 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:Show it:
Fig. 1 einen Längsschnitt durch eine erfindungsgemäße Drehkolbenpumpe ;1 shows a longitudinal section through a rotary piston pump according to the invention.
Fig. 2 eine Ansicht der Drehkolbenpumpe aus Fig. 1 gemäß dem Pfeil I in Fig. 1 undFig. 2 is a view of the rotary piston pump of FIG. 1 according to the arrow I in Fig. 1 and
Fig. 3 einen bekannten Vakuumbremskraftverstärker im Längsschnitt aber anderem Maßstab, als mögliche Anwendung der Erfindung. Beschreibung des AusführungsbeispielsFig. 3 shows a known vacuum brake booster in longitudinal section but other scale, as a possible application of the invention. Description 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.In the illustrated in Fig. 1 rotary piston pump according to the invention a rotatable magnet set 3 is arranged in a cylindrically shaped motor housing 1, said 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 DE 42 41 320 C2 removable. In Fig. 1 of the present application, for the sake of simplicity, the two associated pumps have been shown in a position in which that normally between the power unit and Absperrteil existing working space according to the section plane selected there is not recognizable. 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 nachgeschaltetenThe 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
8 zweiten Pumpe 10, die wiederum auslassseitig mit der Atmosphäre verbunden ist und einlassseitig mit dem Auslass der Pumpe 9.8th 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 shown in Fig. 2, this second pump 10 has an output port 17 to the atmosphere. The first pump is, as indicated by dash-dotted lines, on the inlet side connected to a vacuum brake booster of a motor vehicle shown in Fig. 3. 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 illustrated in Fig. 3 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 erfindungs wesentlich sein.All in the description, the following claims and the drawings illustrated features may be essential to each other, both individually and in any combination with each other.
10 Bezugszahlenliste10 LIST OF REFERENCE NUMBERS
1 Motorgehäuse1 motor housing
2 Motoranker2 motor anchors
3 Magnetsatz3 magnet set
4 Kugellager4 ball bearings
5 Pumpengehäuse5 pump housings
6 Pumpengehäuse6 pump housing
7 O-Ringe7 O-rings
8 Schrauben8 screws
9 Erste Pumpe (größerer Volumenleistung)9 First pump (larger volume capacity)
10 Zweite Pumpe (kleinerer Volumenleistung)10 second pump (smaller volume capacity)
11 Leistungsteil von 911 power unit of 9
12 Leistungsteil von 1012 power section of 10
13 Absperrteil von 913 shut-off part of 9
14 Absperrteil von 1014 shut-off part of 10
15 Lager von 13 und 1415 bearings of 13 and 14
16 Schraubenfeder16 coil spring
17 Ausgangsanschluss17 output connection
18 Leitung18 line
19 Membran19 membrane
20 Unterdruckkammer20 vacuum chamber
21 Arbeitskammer21 working chamber
22 Kolbenstange22 piston rod
23 Arbeitskolben23 working pistons
24 Druckstange24 push rod
25 Doppelventil25 double valve
26 Reaktionskolben26 reaction flasks
11 11

Claims

Ansprüche claims
1. Drehkolbenpumpe für gasförmige Medien1. Rotary lobe pump for gaseous media
- mit einem axial sowie radial gelagerten, als Stirnzahnkugelsegment ausgebildeten und mit einer Antrieb s Vorrichtung (1, 2, 3) verbundenen Leistungsteil (11, 12),- with an axially and radially mounted, formed as a spur ball segment and with a drive s device (1, 2, 3) connected power part (11, 12),
- mit einem, ebenfalls als Stirnzahnkugelsegment ausgebildeten, vom Leistungsteil angetriebenen Absperrteil (13, 14) gleichen radialen Dichtungsdurchmessers,- With a, also designed as Stirnzahnkugelsegment, driven by the power unit shut-off part (13, 14) of the same radial sealing diameter,
- mit durch Kämmen der Zähne des Leistungsteils (11, 12) und jenen des Absperrteils (13, 14) gebildeten Arbeitsräumen zwischen den Teilen,with work spaces between the parts formed by meshing the teeth of the power unit (11, 12) and those of the shut-off member (13, 14),
- wobei Leistungsteil (11, 12) und Absperrteil (13, 14) radial dichtend in einem Pumpengehäuse (5, 6) geführt sind und insbesondere zur Erzielung einer Pumpwirkung bzw. zur Erzeugung eines niedrigen Drucks (Vakuums) auf ihrer miteinander zusammenwirkenden Stirnseite eine jeweils unterschiedliche Anzahl von einem Zahn aufweisen,- Wherein power unit (11, 12) and shut-off (13, 14) radially sealing in a pump housing (5, 6) are guided and in particular for achieving a pumping action or for generating a low pressure (vacuum) on their cooperating end face one each have different numbers of a tooth,
- mit einem linienförmigen, arbeitsraumgrenzenden Formschluss zwischen Flanken und Zahnkämmen der einander gegenüberliegenden zusammenwirkenden Zähne,with a linear, work space delimiting positive connection between flanks and tooth crests of the mutually opposing interacting teeth,
- wobei die Zähne eines der zusammenwirkenden Teile, Leistungsteil (11, 12) oder Absperrteil (13, 14), als Zykloidenteil eine zykloidische Abwicklung ihrer Lauffläche aufweisen,- Wherein the teeth of one of the interacting parts, power part (11, 12) or shut-off part (13, 14), as Zykloidenteil a cycloidal development of their tread,
- wobei die Zähne des jeweils mit dem Zykloidenteil kämmend zusammenwirkenden anderen Teils entsprechende und im Radius frei gestaltbare Zahnkämme aufweisen, welche an den Flanken des Zykloidenteils entlanglaufen und- Wherein the teeth of each co-interacting with the Zykloidenteil cooperating other part and corresponding freely formed in the radius tooth combs, which run along the flanks of Zykloidenteils and
12 - wobei diese aus Leistungsteil (11, 12) und Absperrteil (13, 14) gebildete Pumpe (9, 10) jeweils doppelt vorhanden ist, diese Pumpen (9, 10) gemeinsam angetrieben werden und ihre Arbeitsräume miteinander verbindbar sind, dadurch gekennzeichnet,12 - Wherein these power unit (11, 12) and shut-off (13, 14) formed pump (9, 10) is present in duplicate, these pumps (9, 10) are driven together and their work spaces are connected to each other, characterized
- dass die doppelt vorhandenen Leistungsteile (11, 12) antriebsseitig achsgleich angeordnet sind,- That the double existing power parts (11, 12) are arranged coaxially on the drive side,
- dass ein erstes Leistungsteil (11) von einem antriebsseitig ebenfalls achsgleich in einem Motorgehäuse (1) angeordneten Elektromotor (2, 3) (Spaltmotor) angetrieben wird und- That a first power part (11) of a drive side also coaxially in a motor housing (1) arranged electric motor (2, 3) (gap motor) is driven and
- dass das zweite Leistungsteil (12) drehschlüssig von dem ersten Leistungsteil (11) mitgedreht wird.- That the second power section (12) is rotationally rotated by the first power section (11).
2. Drehkolbenpumpe nach Anspruch 1 , dadurch gekennzeichnet, dass zwischen den Leistungsteilen (11, 12) diese in Richtung Absperrteile (13, 14) hin belastende elastische Mittel (16) angeordnet sind und dass als elastische Mittel insbesondere eine, mit den Leistungsteilen (11, 12) achsgleich angeordnete, Schaubenfeder (16) dient.2. Rotary pump according to claim 1, characterized in that between the power parts (11, 12) in the direction of shut-off parts (13, 14) towards resilient means (16) are arranged and that as an elastic means in particular one, with the power parts (11 , 12) coaxially arranged, Schütze spring (16) is used.
3. Drehkolbenpumpe nach Anspruch 2, dadurch gekennzeichnet, dass für einen Verdrehschluss zwischen den Leistungsteilen eine Steckkupplung dient, welche eine axiale Relativbewegung der Teile (11, 12) zulässt.3. Rotary piston pump according to claim 2, characterized in that for a Verdrehschluss between the power parts a plug-in coupling is used, which permits an axial relative movement of the parts (11, 12).
4. Drehkolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet,4. Rotary pump according to one of the preceding claims, characterized in that
13 dass das Motoranker (2) und Magnetsatz (3) des Elektromotors aufnehmende Motorgehäuse (1) weitgehend zylindrisch ausgebildet ist, wobei deren Stirnseiten durch die beiden Pumpengehäuse (5, 6) verschließbar sind.13 in that the motor armature (2) and magnet set (3) of the electric motor receiving motor housing (1) is substantially cylindrical, wherein the end faces through the two pump housing (5, 6) are closable.
5. Drehkolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die rotierenden Teile (2, 11, 12, 13, 14) in Drehlagern (4,5. Rotary piston pump according to one of the preceding claims, characterized in that the rotating parts (2, 11, 12, 13, 14) in pivot bearings (4,
15) in den Gehäusen angeordnet sind.15) are arranged in the housings.
6. Drehkolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die erste Pumpe (9) jeweils mit deren Absperrteil (13) und ersten Leistungsteil (11) eine größere volumetrische Leistung aufweist, als das die mit gleicher Drehzahl angetriebene zweite Pumpe (10) mit dem zweiten Leistungsteil (12).6. Rotary piston pump according to one of the preceding claims, characterized in that the first pump (9) in each case with the shut-off part (13) and first power part (11) has a greater volumetric power than that driven at the same speed second pump (10) with the second power section (12).
7. Drehkolbenpumpe nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass als Verbindung zur jeweils anderen Pumpe (9, 10) bzw. dem Auslass der ersten und dem Einlass der zweiten Pumpe der im Elektromotor (1, 2, 3) zwischen Magnetsatz (3) und7. Rotary pump according to one of the preceding claims, characterized in that as connection to the respective other pump (9, 10) or the outlet of the first and the inlet of the second pump in the electric motor (1, 2, 3) between the magnet set (3 ) and
Motoranker (2) bzw. Motorgehäuse (1) gebildete Ringraum dient.Motor Anchor (2) or motor housing (1) formed annular space is used.
8. Drehkolbenpumpe nach einem der vorhergehenden Ansprüche,8. Rotary pump according to one of the preceding claims,
14 gekennzeichnet durch deren Anwendung als Vakuumpumpe für einen Bremskraftverstärker eines Kraftfahrzeuges.14 characterized by their use as a vacuum pump for a brake booster of a motor vehicle.
9. Drehkolbenpumpe nach Anspruch 8, dadurch gekennzeichnet, dass vom Einlass der ersten Pumpe (9) ein Anschluss (18) im entsprechenden Pumpengehäuse (5) für eine Leitung zum Bremskraftverstärker vorhanden ist und vom Einlass der zweiten Pumpe (10) ein Anschluss (17) zur Atmosphäre hin besteht.9. rotary piston pump according to claim 8, characterized in that from the inlet of the first pump (9) has a port (18) in the corresponding pump housing (5) for a line to the brake booster and from the inlet of the second pump (10) has a connection (17 ) exists to the atmosphere.
15 15
EP09725577.2A 2008-03-28 2009-03-27 Low pressure pump Active EP2271839B1 (en)

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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

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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
DE9218694U1 (en) * 1991-12-09 1995-03-30 Arnold, Felix, 69239 Neckarsteinach Rotary lobe machine
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
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BRPI0910111A2 (en) 2015-12-29
EP2271839B1 (en) 2015-10-28
JP5101731B2 (en) 2012-12-19
CN101981320A (en) 2011-02-23
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WO2009117993A2 (en) 2009-10-01
CN101981320B (en) 2014-01-22

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