EP2732164A1 - Pompe à engrenages - Google Patents

Pompe à engrenages

Info

Publication number
EP2732164A1
EP2732164A1 EP12746262.0A EP12746262A EP2732164A1 EP 2732164 A1 EP2732164 A1 EP 2732164A1 EP 12746262 A EP12746262 A EP 12746262A EP 2732164 A1 EP2732164 A1 EP 2732164A1
Authority
EP
European Patent Office
Prior art keywords
pump
port
pump housing
port carrier
wheelset
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
EP12746262.0A
Other languages
German (de)
English (en)
Other versions
EP2732164B1 (fr
Inventor
Andreas Blechschmidt
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.)
Nidec GPM GmbH
Original Assignee
Geraete und Pumpenbau GmbH Dr Eugen Schmidt
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 Geraete und Pumpenbau GmbH Dr Eugen Schmidt filed Critical Geraete und Pumpenbau GmbH Dr Eugen Schmidt
Publication of EP2732164A1 publication Critical patent/EP2732164A1/fr
Application granted granted Critical
Publication of EP2732164B1 publication Critical patent/EP2732164B1/fr
Not-in-force 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
    • 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
    • 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
    • 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
    • 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
    • F04C2230/00—Manufacture
    • F04C2230/60—Assembly methods
    • F04C2230/602—Gap; Clearance

Definitions

  • the invention relates to a gerotor pump, in particular for use in small pump units, which are preferably produced by electric motor operated as a modular pump and used in vehicle and engine.
  • Toothed ring pumps for example in the design of gerotor pumps are used in automotive and engine construction, inter alia, in internal combustion engines as fuel pumps or oil pumps.
  • the wheelset used in gerotor pumps consists of an externally toothed inner rotor and an internally toothed outer rotor, wherein the inner rotor is rotatably connected to the drive shaft and having fewer teeth than the outer rotor, and the outer rotor is rotatably mounted in a cylindrical chamber of the pump housing so that the teeth of the eccentric to the outer rotor mounted inner rotor partially mesh with the teeth of the outer rotor.
  • pressure and suction area of the wheelset kidney-shaped pump chambers are arranged in the pump housing, which are connected via connection channels directly to the pump housing arranged pressure and suction connection lines and ensure that the liquid to be pumped from the suction line via the Wheelset is pressed into pressure connection line.
  • US Pat. No. 7,614,227 B2 describes a hydrostatic drive unit of a lawn tractor based on a gerotor pump and a gerotor motor, in which the oil volume flow from the pump to the hydraulic motor is regulated by means of a rotary control valve in the embodiment of a rotary plate.
  • a stationary bearing plate is disposed between the rotary plate and the gerotor motor, in the center of a bearing bore, for rotatably supporting the motor shaft, is arranged.
  • kidney-shaped passage openings are arranged in this bearing plate, in the region of the pump chambers of the gerotor motor, so that the bearing plate at the same time takes over the task of a guide body and in connection with the bearing plate adjacent assemblies, according to the solution presented in US 7,614,227 B2, a Regulation of the traction drive of the lawn tractor, ie a regulation of its speed and its direction of travel, can be guaranteed.
  • gerotor pumps used as oil pumps in the internal combustion engines are used there for engine lubrication, which is known e.g. in motor vehicles over a temperature range of minus 40 ° C to the range of hot idling operation of about 160 ° C must be guaranteed.
  • the pump housings are often die-cast aluminum and the gear sets are made of sintered steel, varying over the wide operating range / temperature range of minus 40 ° C to about 160X, due to the different thermal expansion coefficients of aluminum and steel inevitably also the axial play between the gear set and the pump housing as a function of the current operating temperature. In this case occur at low operating temperatures, due to narrow gaps, usually friction losses and high operating temperatures due to large gaps, losses in volumetric efficiency, which can be up to 50% to 60% of the best for each gerotor pump assembly volumetric efficiency.
  • the volumetric efficiency decreases approximately linearly with increasing temperatures.
  • DE 103 31 979 A1 discloses a toothed ring pump used as an oil pump whose axial clearance is optimized by means of spacer elements arranged in the region of the screw connections between the pump cover and the pump flange in that these spacer elements have a lower thermal expansion coefficient than the pump cover, the pump flange and / or the gear set.
  • a design of a gerotor pump with a smaller outer diameter is known from DE 10 2008 054 758 A1.
  • the invention is therefore based on the object to develop a gerotor pump, which eliminates the aforementioned disadvantages of the prior art, and in particular at small, ie also in the outer diameter of the Housing small pumping units, which are preferably operated by electric motor and manufactured as a modular pump that largely the same Ge Reifenohwel be used in geometry, can be used, wherein the to be developed ring gear pump also according to the customer's request in the timing of the pump manufacturing technology should be easily modifiable , so that always a fluidically optimal behavior of the pump according to the invention is ensured, it should be very inexpensive to produce the ring gear pump to be developed even in very small pump sizes, and also with the use of very cost-effective components, such as pump housings made of aluminum and pump steel, even under extreme operating conditions, such as an oil pump in conjunction with an internal combustion engine, ie over the temperature working range of such oil pump, from about - 40 ° C to about + 160 ° C away, always e ensure optimum axial gap (and thereby minimal losses),
  • Figure 1 an exploded view of an inventive
  • Toothed ring pump in the design of a gerotor pump in a perspective view from above, in the longitudinal direction of the drive shaft 7 from the direction of the housing cover 5;
  • Figure 2 is an exploded view of the ring gear pump according to the invention in the design of a gerotor pump in a perspective view from above and from the direction of the pump housing 1;
  • Figure 3 is an exploded view of the ring gear pump according to the invention in the design of a gerotor pump in a perspective view from the front, from the direction of the drive shaft 7 and the housing cover 5;
  • Figure 4 an assembly drawing of the invention
  • Figure 5 an assembly drawing of the invention
  • Toothed ring pump in the form of a gerotor pump, in the side view, in partial section with the cutting guide according to Figure 4.
  • the invention ring gear pump with a pump housing 1, one arranged in the pump housing 1 Working space 2 with arranged in the end wall 3 of the working space 2 in the pump housing 1 inlet and Ausström Schemeen, arranged on the pump housing 1, sealed by a seal 4 housing cover 5, arranged with a rotatably mounted in the pump housing 1, mounted in a pump bearing 6 drive shaft 7 at a wheelset 8 is arranged, which consists of a rotatably connected to the drive shaft 7 externally toothed inner rotor 9 and an internally toothed outer rotor 10 which is rotatably mounted in a rotor bearing 1 1 in the cylindrical working space 2 of the pump housing 1 such that the teeth of the eccentrically to the outer rotor 10 mounted inner rotor 9 in regions with the teeth of the outer rotor 10 mesh with one or both sides in the suction region of the wheelset 8 arranged / arranged Saugniere / n 12 and one or both sides in the pressure range of the wheelset 8 arranged
  • slidably mounted port carrier 18 is arranged, in which both a suction kidney 12 and a pressure kidney 13 is arranged and both each separated from one another, the port carrier 18 over the entire thickness of the port carrier 18, this in the form of an inlet chamber 19 connected to the suction kidney 12, as well as on the other hand connected to the pressure kidney 13 Ausströmströmhunt 20th penetrate, wherein the thickness of the port carrier 18 corresponds approximately to the thickness of the wheelset 8 and this can also exceed by up to 20%, and the coefficient of thermal expansion of the port carrier 18 is about 70% to 120% higher than the thermal expansion coefficient of the pump housing 1, and that the drive shaft 7, which is non-rotatably connected to the inner rotor 9, by no means protrudes into (or is supported in) the port carrier 18.
  • the port carrier 18 is wear-resistant on the end face adjacent to the wheelset 8 or is wear-resistant coated, or that a sliding plate 25 rotatably connected to the port carrier 18 is arranged between the wheelset 8 and the port carrier 18, whereby between the wheelset 8 and the port carrier 18 in addition to the friction losses and the wear is minimized, so that by means of the solution according to the invention a long service life can be ensured with high efficiency.
  • FIG 1 is shown as one of the possible designs of this feature, arranged between the wheelset 8 and the port carrier 18 sliding plate 25, wherein on the sliding plate 25, a latching nose 26 is arranged, which engages positively with a arranged on the port carrier 18 locking groove 27 in operative connection , And thereby the sliding plate 25 rotatably connected to the port carrier 18.
  • the sliding plate 25 is reduced in its flexural rigidity, thereby better applying and adapting to the wheelset 8 and the port support 18 is possible. simultaneously can be achieved with the shaft guide bore 28, a slight projection of the drive shaft 7.
  • the housing cover 5 via arranged in the pump housing 1 positioning pins 21 and the housing cover 5 associated Positionierkerben 22 against rotation on the pump housing 1, and the port carrier 18 by means of eccentrically arranged in the port carrier 18 pin guide bore 24 and one in the end wall 3 of the working space 2 of Pin guide bore 24 associated arranged guide pin 23 is axially displaceably mounted in the pump housing 1.
  • This arrangement of the invention allows in connection with the inventive arrangement of the port support 18 in the axial direction next to the wheelset 8 of the ring gear pump according to the invention, since the port carrier 18 the inflow and outflow of the pump in its functional geometry maps that in conjunction with the invention, outer cylindrical geometry of the port carrier 18 this easily rotated within certain limits in the pump housing 1, and exactly, eg by guide pins 23 in the pump housing 1, can be positioned securely.
  • the timing of the pump to the particular application of the pump can be optimized fluidically.
  • the port carrier 18 according to the invention also serves to simultaneously ensure optimization of the axial gap.
  • the port carrier 18 whose coefficient of thermal expansion preferably has twice the value of the thermal expansion coefficient of the housing material.
  • the thickness of the port carrier 18 corresponds approximately to the thickness of the wheelset. 8 However, in order to effect an overcompensation of the axial gap with correspondingly desired axial basic play between the wheelset 8 and the port carrier 8, the thickness of the port carrier 18 can be increased, for example, to approximately 120% of the thickness of the wheelset 8.
  • thermoset materials which are e.g. by targeted admixture of friction reducing substances significantly improve the running behavior of the adjacent arranged wheelset.
  • the port carrier 18 is made of sintered and resin-bound sodium chlorides.
  • a predetermined axial thermal expansion of an aluminum pump housing 1 may with a coefficient of thermal expansion for aluminum of about 23 x 10 "6 K" through a port support of sintered and resin-bound sodium chlorides, wherein a thermal expansion coefficient for sodium chloride of about 40 ... 44 x 10 "6 K " 1 , effectively, ie, compensated for with a relatively small thickness dimension of a port carrier 18 made of sintered and resin-bound sodium chloride.
  • the axial gaps depending on the respective operating temperature are always optimized in the entire temperature working range of the pump, i. it is cost effective to ensure optimal dynamic axial gap compensation.
  • the axial gaps are larger at low temperatures and at higher temperatures by significantly greater length expansion of the port carrier 18 to reduce the axial play.
  • Another advantage of the solution according to the invention consists in the fact that in the Axialspaltkompensation invention presented here, the wheelset 8 remains free of axial loads, so that the resulting friction moments are avoided, which inevitably always lead to efficiency losses.
  • the inventively desired temperature-compensating effect of the inventively placed in the axial direction next to the wheelset 8 invention port carrier 18 causes temperature increase and consequent axial growth of the working space 2 in the pump housing 1, in which the wheelset 8 and the port support 18 are housed, that by a clear higher thermal expansion of the port support 18 according to the invention, the axial growth of the working space 2 is balanced with simultaneous attention to the growth of the wheelset 8.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)

Abstract

L'invention concerne une pompe à engrenages, en particulier pour l'utilisation dans de petits groupes de pompes qui fonctionnent de préférence par entraînement par moteur électrique, qui sont fabriquées sous forme de pompes modulaires, et qui sont utilisées pour la construction de véhicules et de moteurs. L'invention a pour but de perfectionner une pompe à engrenages qui puisse être utilisée pour des groupes de pompes construites avec des boîtiers de petits diamètres extérieurs, et qui puisse être modifiée au point de vue temps de fonctionnement de la pompe, suivant le désir du client, de manière simple en technique de production, et qui, y compris lors de l'utilisation de blocs de construction très économiques, tels que des boîtiers de pompe en aluminium, et des engrenages de pompe en acier, même dans les conditions d'utilisation extrêmes d'une pompe à huile, en liaison avec un moteur à combustion interne, garantisse un jeu axial optimal. La pompe à engrenages selon l'invention est caractérisée, en particulier, en ce que le palier de pompe (6) est disposé dans le couvercle de boîtier (5), en ce qu'un support d'orifices (18) monté déplaçable en direction de l'arbre d'entraînement (7) est disposé, bloqué en rotation, dans le boîtier de pompe (1), entre l'ensemble d'engrenages (8) et la paroi frontale (3) du compartiment de travail (2), support d'orifices dans lequel sont disposées, à la fois, un orifice d'aspiration (12) et un orifice de pression (13), les deux traversant séparément l'un de l'autre, le support d'orifices (18), sur toute la largeur de celui-ci (18), l'épaisseur du support d'orifices (18) correspondant environ à l'épaisseur de l'ensemble d'engrenages (8), celle-ci pouvant toutefois être supérieure à 20%, et le coefficient de dilatation thermique du support d'orifices (18) étant d'environ de 70% à 120% supérieur au coefficient de dilatation thermique du boîtier de pompe (1), et en ce que l'arbre d'entraînement (7) lié, solidaire en rotation, avec le rotor intérieur (9) ne pénètre en aucun cas, dans le support d'orifices (18), et en ce que le support d'orifices (18) est configuré, ou recouvert de manière à résister à l'usure, sur la partie frontale adjacente à l'ensemble d'engrenages (8), et/ou en ce qu'une tôle coulissante (25), liée, solidaire en rotation, avec le support d'orifices, est disposée entre l'ensemble d'engrenages (8) et le support d'orifices (18).
EP12746262.0A 2011-07-14 2012-06-27 Pompe à engrenages Not-in-force EP2732164B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102011107157A DE102011107157B4 (de) 2011-07-14 2011-07-14 Zahnringpumpe
PCT/DE2012/000650 WO2013007233A1 (fr) 2011-07-14 2012-06-27 Pompe à engrenages

Publications (2)

Publication Number Publication Date
EP2732164A1 true EP2732164A1 (fr) 2014-05-21
EP2732164B1 EP2732164B1 (fr) 2015-09-09

Family

ID=46651294

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12746262.0A Not-in-force EP2732164B1 (fr) 2011-07-14 2012-06-27 Pompe à engrenages

Country Status (5)

Country Link
US (1) US9309885B2 (fr)
EP (1) EP2732164B1 (fr)
DE (1) DE102011107157B4 (fr)
ES (1) ES2553790T3 (fr)
WO (1) WO2013007233A1 (fr)

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Publication number Priority date Publication date Assignee Title
WO2016185329A1 (fr) * 2015-05-20 2016-11-24 Casappa S.P.A. Pompe à engrenages et son procédé de réalisation
ITUB20159726A1 (it) * 2015-12-22 2017-06-22 Bosch Gmbh Robert Gruppo di pompaggio per alimentare combustibile, preferibilmente gasolio, ad un motore a combustione interna
CN109969259B (zh) * 2017-12-28 2021-06-18 比亚迪股份有限公司 电动油泵总成和具有其的车辆
CN111183287B (zh) 2018-02-14 2022-04-01 斯泰克波尔国际工程产品有限公司 带芯轴的摆线泵
DE102018210415A1 (de) * 2018-05-08 2019-11-14 Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg Elektrische Fluidpumpe und Kraftfahrzeuggetriebe
USD923060S1 (en) 2018-08-09 2021-06-22 Psg Germany Gmbh Pump
US10247295B1 (en) * 2018-10-22 2019-04-02 GM Global Technology Operations LLC Transfer case oil pump assembly
USD966342S1 (en) * 2020-02-07 2022-10-11 Pedrollo S.P.A. Electric pump
USD960203S1 (en) * 2020-09-28 2022-08-09 Hugo Vogelsang Maschinenbau Gmbh Pump for liquids
US11661938B2 (en) * 2021-08-31 2023-05-30 GM Global Technology Operations LLC Pump system and method for optimized torque requirements and volumetric efficiencies

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US3128707A (en) * 1960-03-11 1964-04-14 Robert W Brundage Multiple discharge hydraulic pump
GB943624A (en) 1960-10-05 1963-12-04 Doulton & Co Ltd Permeable plastic materials
US3805526A (en) * 1972-11-03 1974-04-23 Aplitec Ltd Variable displacement rotary hydraulic machines
JPH07208348A (ja) * 1994-01-27 1995-08-08 Brother Ind Ltd ポンプ
DE19720286A1 (de) 1997-05-15 1998-11-19 Winter Gmbh Gehäuse mit einem unregelmäßigen Hohlraum und Verfahren zur Herstellung eines derartigen Gehäuses
US6769889B1 (en) * 2003-04-02 2004-08-03 Delphi Technologies, Inc. Balanced pressure gerotor fuel pump
DE10331979A1 (de) 2003-07-14 2005-02-17 Gkn Sinter Metals Gmbh Pumpe mit optimiertem Axialspiel
US7614227B2 (en) * 2006-08-04 2009-11-10 Briggs And Stratton Corporation Rotary control valve for a hydrostatic transmission
DE102008054758A1 (de) 2008-12-16 2010-06-17 Robert Bosch Gmbh Förderaggregat

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Title
See references of WO2013007233A1 *

Also Published As

Publication number Publication date
EP2732164B1 (fr) 2015-09-09
DE102011107157B4 (de) 2013-02-28
US9309885B2 (en) 2016-04-12
WO2013007233A4 (fr) 2013-03-07
WO2013007233A1 (fr) 2013-01-17
DE102011107157A1 (de) 2013-01-17
US20140154125A1 (en) 2014-06-05
ES2553790T3 (es) 2015-12-11

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