EP2271839A2 - Pompe basse pression - Google Patents

Pompe basse pression

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)
English (en)
Other versions
EP2271839B1 (fr
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/fr
Application granted granted Critical
Publication of EP2271839B1 publication Critical patent/EP2271839B1/fr
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

L'invention concerne une pompe basse pression/pompe à vide destinée à des milieux gazeux et comprenant deux parties s'engrenant réalisées avec leurs dents sous forme d'élément cycloïdal, ces étages compresseurs présents en double étant reliés entre eux. Une partie puissance des pompes/compresseurs est entraînée et la partie puissance de l'autre pompe/compresseur placée coaxialement est entraînée avec elle par solidarité de rotation.
EP09725577.2A 2008-03-28 2009-03-27 Pompe basse pression Active EP2271839B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102008016293A DE102008016293A1 (de) 2008-03-28 2008-03-28 Niederdruckpumpe
PCT/DE2009/000394 WO2009117993A2 (fr) 2008-03-28 2009-03-27 Pompe basse pression

Publications (2)

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

Family

ID=41011163

Family Applications (1)

Application Number Title Priority Date Filing Date
EP09725577.2A Active EP2271839B1 (fr) 2008-03-28 2009-03-27 Pompe basse pression

Country Status (7)

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

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011087606A1 (de) * 2011-12-01 2013-06-06 Robert Bosch Gmbh Kraftfahrzeugsystemeinrichtung sowie Verfahren zum Betreiben einer Kraftfahrzeugsystemeinrichtung
DE102014209140A1 (de) * 2013-05-23 2014-11-27 Robert Bosch Gmbh Förderaggregat

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 (de) 1966-02-21 1967-12-31 Wildhaber Ernest Verdrängungsmaschine
US3817666A (en) * 1973-02-12 1974-06-18 E Wildhaber Rotary positive displacement unit
US5513969A (en) * 1991-12-09 1996-05-07 Arnold; Felix Rotary piston machine having engaging cycloidal gears
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 (de) * 2005-03-16 2006-09-21 Cor Pumps + Compressors Ag Drehkolbenmaschine
EP2016287B1 (fr) * 2006-05-10 2018-07-11 Robert Bosch GmbH Machine a piston rotatif

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2009117993A2 *

Also Published As

Publication number Publication date
WO2009117993A3 (fr) 2010-04-01
CN101981320A (zh) 2011-02-23
JP2011515617A (ja) 2011-05-19
EP2271839B1 (fr) 2015-10-28
WO2009117993A2 (fr) 2009-10-01
US20110052438A1 (en) 2011-03-03
US9022752B2 (en) 2015-05-05
DE102008016293A1 (de) 2009-10-01
BRPI0910111B1 (pt) 2019-10-29
CN101981320B (zh) 2014-01-22
JP5101731B2 (ja) 2012-12-19
BRPI0910111A2 (pt) 2015-12-29

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