EP1081382B1 - Machine à engrenages - Google Patents

Machine à engrenages Download PDF

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Publication number
EP1081382B1
EP1081382B1 EP00117962A EP00117962A EP1081382B1 EP 1081382 B1 EP1081382 B1 EP 1081382B1 EP 00117962 A EP00117962 A EP 00117962A EP 00117962 A EP00117962 A EP 00117962A EP 1081382 B1 EP1081382 B1 EP 1081382B1
Authority
EP
European Patent Office
Prior art keywords
shaft
pressure side
seal
gear
axial
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP00117962A
Other languages
German (de)
English (en)
Other versions
EP1081382A3 (fr
EP1081382A2 (fr
Inventor
Klaus Griese
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 EP1081382A2 publication Critical patent/EP1081382A2/fr
Publication of EP1081382A3 publication Critical patent/EP1081382A3/fr
Application granted granted Critical
Publication of EP1081382B1 publication Critical patent/EP1081382B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps

Definitions

  • the invention is based on a gear machine with the Features of the preamble of claim 1, as in DE 2 847 711.
  • External gear machines usually have a housing, the an interior, in which at least one gear arrangement with at least a first and a second gear is arranged, which mesh with each other in external engagement.
  • the first gear is mounted on a shaft, which on one Drive side out and over a shaft seal is sealed.
  • the second gear is on an axis attached. The axis and the shaft are in cover plates of the Housing or stored in bushings.
  • gears between Distinguished fore and aft edges.
  • leading edges transmit the rotational movement between the driving and driven gear.
  • the medium to be promoted becomes in tooth gaps of the gears from a low pressure side too promoted a high pressure side.
  • Flank contact points migrate the teeth of the gear pair along an engagement line.
  • the meshing tooth flanks prevent one from engaging Return flow of the medium from the high pressure side to the low pressure side.
  • the gears are pressurized oil in one Feed fed, whereby at the outwardly guided wave Torque can be tapped.
  • a radial seal of the gears of an external gear machine is usually pressure-dependent.
  • the operating pressure on the High pressure side acts in the circumferential direction over a forming crescent-shaped gap on the two gears and pushes the axle and the shaft of the gears with a pressure-dependent operating force in the bearing bushes or in the Cover plates radially inward against the low pressure side.
  • a defined shrinkage takes place the tooth tips in the housing on the low pressure side, i. the Gears perform a kind of milling operation.
  • On the Low pressure side arise sealing zones with an optimal Seal gap. The resulting chips are controlled discharged to the outside with the oil flow.
  • An axial sealing of the gears is also pressure-dependent, by respectively the outsides of the on the drive side arranged and the one on the opposite side arranged bearing bushes subjected to the operating pressure be and the bushings defined contact forces in the axial Exercise direction on the side surfaces of the gears.
  • the Bushings are axially displaceable and have on their Outer sides each axial pressure fields, which in the bearing bushes cast in, milled in and / or by special axial field seals can be formed. The pressure acts on the Bearing bushes in the exactly limited Axialdruckfeldern contrary the internal hydraulic forces.
  • the Axialscherfelder or Axialfelddichtitch the bearing bushes on the drive side and the Axialfelddichtitch the Bushings on the opposite side are usually identical, but each executed asymmetrically.
  • the Axial field seals each limit an axial pressure field the high pressure side and a field open to the shaft and to the axle on the low pressure side. Leakage oil from the high pressure side can be discharged on the low pressure side.
  • the high pressure side and the low pressure side are fixed, creating a Reverse operation is not possible. This also applies to Operation of the gear machine as a motor.
  • a shaft seal in front of the shaft seal is unsymmetrical Axial field seals connected to the low pressure side, i.e. for gear pumps with the inlet side and gear motors with the drain side. Especially with gear motors can during operation on the low pressure side or drain side Pressure peaks occur, for example, by vibrations of a Valve and / or in a case of resonance, etc., over the Shaft sealing space can act on the shaft seal.
  • DE 29 17 384 A discloses a vane pump in which a shaft sealing chamber via a valve with the suction chamber of the pump is connectable.
  • the valve is like a check valve constructed and arranged so that it towards the shaft seal chamber locks. It has the task of reproducing one Low pressure in the suction chamber of the vane pump in the Shaft seal to prevent and is therefore probably as Pressure relief valve referred to. This is because in the suction room maximum negative pressure of 1 bar may occur be set at least 1 bar.
  • it is preferably set to 1 to 2 bar, so that in normal operation in the shaft seal against the environment an overpressure of 1 to 2 bar prevails.
  • the invention relates to a gear machine, in particular from a gear motor, with a housing that has an interior in which at least one gear arrangement with at least a first and a second gear is arranged in the Combine external engagement with each other.
  • the first gear is on attached to a shaft, on a drive side to the outside guided and sealed by a shaft seal.
  • the second gear is arranged on an axis.
  • the gear machine has a first axial field seal on the the drive side opposite side of the gears Axialdruckfeld on a high pressure side and one to the shaft and bounded to the axis open field on a low pressure side, and with a second axial field seal on the drive side of the Gears limited an axial pressure field on a high pressure side.
  • the second axial field seal a Wellendichtraum before the shaft seal to the high pressure side and seals to a low pressure side of the gear machine and that for leakage oil discharge the shaft seal chamber via a channel with a closing in the direction of shaft seal check valve with the limited by the first axial field seal, to the shaft and connected to the axis open field on the low pressure side is.
  • Pressure peaks in the shaft seal chamber are through the second Axial field seal on the drive side and through the check valve avoided.
  • the leak oil can with a particularly simple and low-cost duct system discharged to the low pressure side become. Leakage pipes on the drive side opposite side in the case or in a lid can be avoided.
  • the leak oil can pass through a line in the housing to the low pressure side the first axial field seal to be passed or particularly advantageous by a channel in the axis.
  • the channel can be introduced easily and inexpensively, in particular by drilling.
  • essentially standard components a one-way gear machine used as in particular the housing, an asymmetrical axial field seal and a cover on the drive side opposite side of the gears, etc.
  • On the drive side is advantageously a symmetrical axial field seal of a reversible gear motor used.
  • the check valve can be at various, the skilled as be attached meaningful sites, for example in a stepped bore in the axis, etc. Particularly advantageous However, the check valve is in a cover mounted on the drive side, causing an increase in the rotating mass is avoided by the check valve.
  • the gear machine according to the invention is preferably as unidirectional gear motor used in systems in which the low pressure side increases pressure fluctuations or Pressure peaks can occur, especially in ventilation systems of motor vehicles.
  • Fig. 1 shows a gear motor with a housing 10, a Interior 12, which is attached by two on the housing 10 Lids 52, 54 is limited.
  • a Gear arrangement 14 arranged, the two in the outer engagement having meshing gears 16, 18.
  • the abortive Gear 16 is rotatably connected to an output shaft 24, about it over each a bearing shell 56, 58 in two Bearing bushes 60, 62 is mounted in the housing 10.
  • the output shaft 24 is on a driven side 20 through the lid 52nd guided to the outside and sealed by a shaft seal 22.
  • the gear 18 is rotatably connected to an axis 26, about it via a respective bearing shell 64, 66 in two bushings 68, 70 is mounted in the housing 10.
  • the bearing bushes 60, 68 and the bushings 62, 70 may also be in one piece be executed.
  • the geared motor is driven on a high pressure side 42, 72 in a feed 74 shown schematically with pressure medium acted upon (Fig. 2 and 3).
  • the pressure medium is from the High pressure side 42, 72 in tooth gaps of the gears 16, 18 outside along the housing 10 to a low pressure side 34, 44th guided and drives the gears 16, 18 at.
  • On the Low pressure side 34, 44 dive the teeth and gaps in each other and displace the pressure medium into a schematic illustrated sequence 76.
  • a radial seal of the gears 16, 18 of the external gear motor is pressure dependent.
  • the operating pressure on the High pressure side 42, 72 acts in the circumferential direction over a forming crescent-shaped gap on the two gears 16, 18 and presses the axis 26 and the shaft 24 of the gears 16, 18 in the bearing bushes 60, 62, 68, 70 radially inwardly against the low pressure side 34, 44 with a pressure dependent Operating force.
  • On the low pressure side 34, 44 arise Sealing zones with an optimum sealing gap.
  • An axial sealing of the gears 16, 18 also takes place depending on the pressure, each by the outer sides of the on the output side 20 arranged and the one on the opposite Page 30 arranged bearing bushes 60, 62, 68, 70 with the Operating pressure is applied and the bearing bushes 60, 62, 68, 70 defined contact forces in the axial direction the side surfaces of the gears 16, 18 exercise.
  • the bearing bushes 60, 62, 68, 70 are axially displaceable and have on their outsides each Axialdruckfelder 32, 38, the are limited by axial field seals 28, 36.
  • the lids 52, 54 and the housing 10 are outwardly via a respective Housing seal 78, 80 sealed.
  • the pressure acts on the Bushings 60, 62, 68, 70 in the exactly limited Axialdruckfeldern 32, 38 against the inner hydraulic Forces.
  • the axial field seal 28 on the output side 20 opposite Page 30 limits the Axialdruckfeld 32 on the High pressure side 72 and a shaft 24 and the axis 26 open Box 84 on the low pressure side 34 (Fig. 2). Leakage oil from the high pressure side 72 can on the low pressure side 34 in the Drain 76 are discharged.
  • a shaft seal chamber 40 in front of the shaft seal 22 to the high pressure side 42 and the low pressure side 44 from ( Figures 1 and 3).
  • For leakage oil removal is the shaft seal chamber 40 via a channel 46 with a toward shaft sealing chamber 40 closing check valve 48 with that of the first Axial field seal 28 limited to the shaft 24 and the axis 26 open field 84 on the low pressure side 34 connected.
  • On the shaft seal 22 always acts only the static pressure in Run 76, while pressure peaks in the shaft seal chamber 40 through the axial field seal 36 on the output side 20 and through the check valve 48 can be avoided, the pressure peaks in the drain 76 closes and protects the shaft seal 22.
  • the leaked into the shaft seal 40 leakage oil is on the the output side 20 opposite side 30 via the channel 46, which essentially consists of a schematic illustrated drain line 82 in the lid 52 and from a Bore 50 in the axis 26 consists. Holes and channels in Lid 54 can be avoided.
  • the check valve 48 is disposed in the drain line 82 in the lid 52.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Hydraulic Motors (AREA)
  • General Details Of Gearings (AREA)
  • Gear Transmission (AREA)

Claims (3)

  1. Machine à engrenage, en particulier moteur à engrenage, comprenant un corps (10) qui présente un volume intérieur (12) dans lequel est disposé au moins un jeu de roues dentées (14) comprenant au moins une première et une seconde roue dentée (16, 18) qui engrènent entre elles en prise extérieure, la première roue dentée (16) étant calée sur un arbre (24) qui se prolonge vers l'extérieur sur un côté d'entraínement (20) et est monté à joint étanche au moyen d'une garniture d'étanchéité d'arbre (22), et la seconde roue dentée (18) étant disposée sur un axe (26), une première garniture d'étanchéité de zone axiale (28) qui, sur le côté (30) des roues dentées (16, 18) à l'opposé du côté d'entraínement (20), limite une zone de pression axiale (32) sur un côté haute pression (72) et une zone (84) ouverte sur l'arbre (24) et sur l'axe (26) sur un côté basse pression (34), et une seconde garniture d'étanchéité de zone axiale (36) qui, sur le côté d'entraínement (20) des roues dentées (16, 18), limite une zone de pression axiale (38) sur un côté haute pression (42),
    caractérisée en ce que
    la seconde garniture d'étanchéité de zone axiale (36) isole à joint étanche un espace d'étanchéité d'arbre (40) en amont de la garniture d'étanchéité d'arbre (22) par rapport au côté haute pression (42) et par rapport à un côté basse pression (44) et, pour l'évacuation de l'huile de fuite, l'espace d'étanchéité d'arbre (40) est relié, par un canal (46) équipé d'un clapet anti-retour (48) qui se ferme en direction de l'espace d'étanchéité d'arbre (40), à la zone (84) limitée par la première garniture d'étanchéité de zone axiale (28) qui est ouverte sur l'arbre (24) et l'axe (26) sur le côté basse pression (34).
  2. Machine à engrenage selon la revendication 1,
    caractérisée en ce que
    l'huile de fuite est conduite par un canal (50) pratiqué dans l'axe (26) au côté (30) des roues dentées (16, 18) à l'opposé du côté d'entraínement (20).
  3. Machine à engrenage selon la revendication 1 ou 2,
    caractérisée en ce que
    le clapet anti-retour (48) est disposé dans un couvercle (52) sur le côté d'entraínement (20).
EP00117962A 1999-09-04 2000-08-22 Machine à engrenages Expired - Lifetime EP1081382B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19942297A DE19942297A1 (de) 1999-09-04 1999-09-04 Zahnradmaschine
DE19942297 1999-09-04

Publications (3)

Publication Number Publication Date
EP1081382A2 EP1081382A2 (fr) 2001-03-07
EP1081382A3 EP1081382A3 (fr) 2002-08-07
EP1081382B1 true EP1081382B1 (fr) 2005-07-20

Family

ID=7920844

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00117962A Expired - Lifetime EP1081382B1 (fr) 1999-09-04 2000-08-22 Machine à engrenages

Country Status (2)

Country Link
EP (1) EP1081382B1 (fr)
DE (2) DE19942297A1 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005056909A1 (de) * 2005-11-29 2007-05-31 Bosch Rexroth Ag Hydraulische Zahnradmaschine
DE202009001525U1 (de) * 2009-02-06 2010-06-24 Inatec Gmbh Zahnradpumpe
DE102010055682A1 (de) 2010-12-22 2012-06-28 Robert Bosch Gmbh Gehäuse einer Außenzahnradmaschine und Außenzahnradmaschine
DE102016225883A1 (de) * 2016-12-21 2018-06-21 Robert Bosch Gmbh Zahnradpumpe für ein Abwärmerückgewinnungssystem

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2487732A (en) * 1948-02-19 1949-11-08 Borg Warner Pump-pressure loaded-with unloading relief valve
DE1155339B (de) * 1956-09-06 1963-10-03 Bosch Gmbh Robert Zahnradfluessigkeitspumpe
US3156191A (en) * 1960-12-23 1964-11-10 Clark Equipment Co Sealing means for pumps and motors
DE2847711A1 (de) * 1978-11-03 1980-05-14 Bosch Gmbh Robert Zahnradmaschine (pumpe oder hydromotor)
DE2917384A1 (de) * 1979-04-28 1980-10-30 Zahnradfabrik Friedrichshafen Hydraulikpumpe, insbesondere fluegelzellenpumpe
DE3938135A1 (de) * 1989-11-16 1991-05-23 Bosch Gmbh Robert Zahnradpumpe
DE4209980A1 (de) * 1992-03-27 1993-09-30 Bosch Gmbh Robert Reversierbare Zahnradmaschine

Also Published As

Publication number Publication date
EP1081382A3 (fr) 2002-08-07
DE19942297A1 (de) 2001-03-08
DE50010738D1 (de) 2005-08-25
EP1081382A2 (fr) 2001-03-07

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