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WO2008135326A1 - Pompe à engrenage - Google Patents

Pompe à engrenage Download PDF

Info

Publication number
WO2008135326A1
WO2008135326A1 PCT/EP2008/053968 EP2008053968W WO2008135326A1 WO 2008135326 A1 WO2008135326 A1 WO 2008135326A1 EP 2008053968 W EP2008053968 W EP 2008053968W WO 2008135326 A1 WO2008135326 A1 WO 2008135326A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
drive shaft
sealing
shaft
bearing
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.)
Ceased
Application number
PCT/EP2008/053968
Other languages
German (de)
English (en)
Inventor
Ulrich Helbing
Arkardiusz Tomzik
Dietrich Witzler
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.)
Oerlikon Textile GmbH and Co KG
Original Assignee
Oerlikon Textile GmbH and Co KG
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 Oerlikon Textile GmbH and Co KG filed Critical Oerlikon Textile GmbH and Co KG
Priority to DE502008001091T priority Critical patent/DE502008001091D1/de
Priority to AT08735717T priority patent/ATE476600T1/de
Priority to US12/598,322 priority patent/US20100196186A1/en
Priority to EP08735717A priority patent/EP2140142B1/fr
Publication of WO2008135326A1 publication Critical patent/WO2008135326A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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
    • 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
    • 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
    • F04C15/0034—Sealing arrangements in rotary-piston machines or pumps for other than the working fluid, i.e. the sealing arrangements are not between working chambers of the machine
    • F04C15/0038—Shaft sealings specially adapted for 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
    • 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
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
    • 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
    • F04C2220/24—Application for metering throughflow

Definitions

  • the invention relates to a gear pump for conveying colored lakes according to the preamble of claim 1.
  • a generic gear pump is known from EP 1 280 996 Bl.
  • the known gear pump has two meshing gears, which are rotatably supported within a pump housing.
  • One of the gears is coupled to a drive shaft which is mounted in a bearing within the pump housing.
  • the drive shaft penetrates the bearing housing in the pump housing and is coupled outside of the pump housing with a drive.
  • the gear wheel on the drive shaft is assigned a sealing means which seals the bearing means of the drive shaft relative to a delivery space formed on the circumference of the gear wheel.
  • the sealing means on a ceramic ring which is supported under a bias on a front side of the gear.
  • a further gear pump for conveying and metering dye lakes is known, in which on both end sides of the driven gear sealing means are arranged in the pump housing to separate the delivery area within the pump housing from the storage area of the drive shaft.
  • the sealant is in this case formed by a seal and a spring element, which loads the seal with a small force in the direction of the gear.
  • Another object of the invention is to provide a gear pump of the generic type in which the bearing friction of the drive shaft remains substantially constant during operation.
  • the invention has the particular advantage that the driven gear is guided freely in the pump housing and forms a relatively uniform sealing gap to each end face with the pump housing.
  • a second sealing means is arranged with a second pressure ring on the opposite end face of the gear on the circumference of the drive shaft between a second bearing means and the gear, both pressure rings on both end sides of the gear each having a sealing shoulder and loading by a spring means on the end faces of the gear are pressed.
  • the gear is stretched between the pressure rings and thus independent of the position of the drive shaft. A tarnishing of one of the end faces on one of the housing plates is thereby avoided and the gearwheel forms an equally large sealing gap with the pump housing for each end face.
  • the prestressed on both sides of the pressure rings and the thus fixed position of the gear allows a high sealing effect, so that the protruding from the pumping chamber color lakes advances only in the lateral sealing gaps only to the sealing shoulders of the pressure rings.
  • the bearing means within the pump housing remain free of color lakes, so that a flushing of the bearing points of the drive shaft is unnecessary. In the design of the storage means thus the requirements of a flushability can be neglected.
  • the sealing means each have a sealing ring, which to the bearing means Shield both sides of the gear relative to the pressure rings and each define on the circumference of the drive shaft between a see the pressure ring and the sealing ring formed Spülraum.
  • the sealing rings which are arranged on the circumference of the drive shaft and sealingly act between the pump housing and the drive shaft, form a second den Pressure rings downstream seal to separate the bearings of the delivery chamber.
  • each of the flushing chambers is connected by a flushing channel in the pump housing with a flushing connection.
  • the color varnishes which have entered the rinsing chamber can be rinsed out before a color change by means of a rinsing liquid supplied via the rinsing connection.
  • the two rinsing through several flushing channels between the drive shaft and the pressure rings and between see the drive shaft and the gear together connect to.
  • the bearing means can run through bushes for sliding storage of the drive shaft, but in the case of bearing lubrication borrowed funds are used.
  • the bearing means for supporting the drive shaft are preferably formed according to an advantageous embodiment of the invention by at least two rolling bearings whose rolling elements are held in a filled with a lubricant annular chamber. As a lubricant fat fills are preferably used, so that the drive shaft can be driven with relatively low bearing friction.
  • the bearing means of the shaft journal can also be shielded by sealing rings relative to the pressure rings in such a way that no residues of color lakes pollute the bearing means.
  • the sealing rings form with the pressure rings on the circumference of the shaft journal to each end face of the gear each have a flushing chamber, which is connected by a flushing passage in the pump housing with a flushing port.
  • the two rinsing chambers are connected by a plurality of purge channels between the shaft journal and the pressure rings and between the shaft journal and the gear.
  • the bearing means for supporting the shaft journal are preferably formed identically to the bearing means of the drive shaft. So a plain bearing with bushings would be possible.
  • the bearing means for supporting the shaft journal are preferably formed by at least two roller bearings whose rolling elements are held in an annular chamber filled with a lubricant.
  • the pressure rings are formed of a ceramic material and the sealing rings designed as so-called U-rings.
  • the biasing force generated by the spring means is generated by the spring means, with which a sealing shoulder of the pressure ring is held on the end face of the gear. It is essential that the generated biasing force during the operating life of the pump remains substantially constant.
  • the spring means is formed by a respective plate spring assembly. In this case, high spring forces can be generated even in small spaces in the scope of the drive shaft or the shaft journal.
  • the pump housing is preferably designed in several parts, the end sides of the gear wheels being held between two housing plates.
  • the plate design allows a Feinstbearbeitung of the pump housing, so that a high plane parallelism between the gears and the housing plates is adjustable.
  • the drive shaft of a bearing shaft and a coupling shaft connected by a releasable rotational connection with the bearing shaft wherein the bearing shaft is connected within the pump housing with the gear and is supported by the bearing means.
  • the clutch shaft outside of the pump housing is in contrast mounted rotatably in a support housing by a support bearing and can be coupled at the free end to the drive.
  • Fig. 1 shows schematically a sectional view of a first embodiment of the gear pump according to the invention
  • FIG. 2 schematically shows a sectional view of the shaft journal of the exemplary embodiment from FIG. 3
  • Fig. 3 shows schematically a sectional view of another embodiment of the gear pump according to the invention
  • FIG. 4 is a schematic sectional view of the drive shaft of the embodiment from FIG. 1
  • a first embodiment of the inventive gear pump is shown in a schematic sectional view.
  • Fig. 2 shows only an enlarged detail of Fig. 1, so that the following description applies to both figures.
  • the gear pump has a pump housing 1, which is constructed in several parts and the housing plates 1.1 and 1.2 and between the housing plate 1.1 and
  • the middle plate 1.3 has recesses for two intermeshing gears 4 and 5.
  • a delivery channel system 6 is formed in the housing parts, which is connected to a pump inlet 2 formed in the housing plate 1.2 and with a pump outlet 3 formed in the housing plate 1.1.
  • the delivery channel system 6 is preferably formed by bores and recesses in the housing plates 1.1 and 1.2 and the center plate 1.3.
  • the gear 4 is rotatably connected to a drive shaft 7.
  • the gear 4 is penetrated in a central bore 28 of the drive shaft 7.
  • a connecting means 29 (shown in phantom), through which a positive and rotationally fixed connection between the drive shaft 7 and the gear 4 is formed.
  • the drive shaft 7 has a bearing end 7.1 within the pump housing 1 and a coupling end 7.2 outside of the pump housing 1.
  • a continuous receiving bore 18 is provided in the housing plate 1.1 and in the housing plate 1.2, which is penetrated substantially coaxially by the drive shaft 7.
  • a sealing means 9.1 and 9.2 as well as a bearing means 8.1 and 8.2 are respectively arranged between the circumference of the drive shaft 7 and the receiving bore 18 of the housing plates 1.1 and 1.2.
  • Each of the sealing means 9.1 and 9.2 in each case has a pressure ring 10.1 and 10.2.
  • the pressure rings 10.1 and 10.2 are held axially displaceably on the circumference of the drive shaft 7 and are supported by a respective sealing shoulder 16.1 and 16.2 on the end faces of the gear 4.
  • the pressure rings 10.1 and 10.2 and the end faces of the gear 4 are for this purpose preferably formed of a ceramic material.
  • the gear 4 and the pressure rings 10.1 and 10.2 may also be formed entirely of a ceramic material.
  • each have a spring means 11.1 and 11.2 is arranged at the opposite to the sealing shoulder 16.1 and 16.2 side of the pressure rings 10.1 and 10.2 each have a spring means 11.1 and 11.2 is arranged.
  • the Fe derstoff 11.1 which is formed in this embodiment as a plate spring package is stretched between a fixed in the housing plate 1.1 retaining ring 17 and the pressure ring 10.1.
  • the spring means 11.2 which is also designed as a disc spring assembly, between a further fixed in the housing plate 1.2 retaining ring 17 and the pressure ring 10.2 acts.
  • the sealing rings 12.1 and 12.2 are formed in this embodiment by grooved rings that generate radially acting sealing forces between the drive shaft 7 and the receiving holes 18.
  • the sealing rings 12.1 and 12.2 are held at a distance from the pressure rings 10.1 and 10.2 on the circumference of the drive shaft 7, so that in the space between the drive shaft 7 and the receiving bore 18, a washing compartment 13.1 and 13.2 is formed.
  • the washing compartment 13.1 is coupled via a flushing channel 14.1 in the housing plate 1.1 with a flushing connection 15.1.
  • the washing compartment 13.2 formed in the sealing means 9.2 on the opposite side of the toothed wheel 4 is connected to a flushing connection 15.2 via a flushing channel 14.2 in the housing plate 1.2.
  • the flushing connections 15.1 and 15.2 are connected to a flushing system.
  • the rinsing rooms 13.1 and 13.2 are connected to one another by a plurality of rinsing grooves 36.1 and 36.2.
  • the flushing grooves 36.1 here each denote the flushing groove, which extend between the pressure ring 10.1 and the drive shaft 7 and the pressure rings 10.2 and the drive shaft 7.
  • the flushing groove 36.1 may be formed by a groove on the circumference of the drive shaft or by a groove on the inner diameter of the pressure ring.
  • the flushing groove 36.2 denotes a connection between the end faces of the gear 4, wherein this through a groove in the bore 28th of the gear 4 or by a groove on the circumference of the drive shaft 7 may be executed.
  • the bearing means 8.1 and 8.2 respectively in the outer regions of the housing plates 1.1 and 1.2 are arranged.
  • the bearing means 8.1 and 8.2 are each formed by rolling bearings 32, which has a plurality of rolling elements 30 which are held in a closed annular chamber 31 between an inner and an outer race.
  • the roller bearings 32 are held in the axial direction by a respective retaining ring 17 fixed in the housing plate 1.1 and 1.2.
  • the closed annular chamber 31 is preferably a grease filling, which preferably ensures the lubrication of the rolling elements during the service life of the gear pump.
  • the Aufhahmebohrung 18 in the housing plate 1.1 is closed to the outside by a cover 27.
  • the coupling end 7.2 of the drive shaft 7 protrudes from the receiving bore 18 of the housing plate 1.2 out.
  • the coupling end 7.2 of the drive shaft 7 has in the end region a diameter shoulder 33 on which a support ring 20 rests.
  • the support ring 20 is L-shaped and is held in a recess of a support housing 19.
  • the support housing 19 has a recess 21, which is completely penetrated by the drive shaft 7, so that the free coupling end 7.2 of the drive shaft 7 protrudes to connect a drive from the support housing 19.
  • the support housing 19 is fixedly connected to the pump housing 1.
  • the gear 4 driven by the drive shaft 7 is in engagement with the gear 5, which is held freely rotatably between the housing plates 1.1 and 1.2 in the center plate 13.
  • the gear 5 is held with its bore on a bearing journal 34.
  • the bearing pin 34 is not supported in the housing plates 1.1 and 1.2 in this example, so that the gear 5 only through the housing plates 1.1 and 1.2 and guided by the center plate 1.3 and is driven by the gear 4.
  • Delivery channel system 6 is conveyed under pressure to the pump outlet 3. The from the conveyor channel 6 via the gaps between the end faces of the gears 4 and
  • a rinsing liquid is introduced into the pump housing via the rinsing connections 15.1 and 15.2 and the spaces between the drive shaft 7 , the housing plates 1.1 and 1.2 and rinsed in the gear 4.
  • the delivery channel system 6 within the pump housing is also flushed by means of a flushing liquid through the pump inlet 2 and the pump outlet 3, so that the gaps between the gears 4 and the housing plates 1.1 and 1.2 and the center plate 1.3 can be flushed.
  • a further embodiment of the inventive gear pump is shown schematically in a cross-sectional view.
  • the components with the same functions have been given identical reference numerals.
  • Fig. 4 is an enlarged view of a portion of Fig. 3, so that the following description applies to both figures.
  • the drive shaft 7 connected in a rotationally fixed manner to the toothed wheel 4 is formed by a bearing shaft 25 and a coupling shaft 26, which are connected to one another by a rotary joint 24.
  • the bearing shaft 25 is rotatably supported by the bearing means 8.1 and 8.2 in the receiving bores 18 of the housing plates 1.1 and 1.2.
  • the sealing means 9.1 and 9.2 associated with the bearing means 8.1 and 8.2 on the circumference of the bearing shaft 25 as well as the bearing means 8.1 and 8.2 are identical to the preceding embodiment, so that reference can be made to the preceding description.
  • the bearing shaft 25 extends substantially over the width of the housing plates 1.1 and 1.2, wherein on the drive side, the bearing shaft 25 is coupled to the coupling shaft 26.
  • 26 projections are formed at the ends of the bearing shaft 25 and the coupling shaft, which constitute the rotary joint 24.
  • the coupling shaft 26 is rotatably supported by a support bearing 22 in a support housing 19.
  • the coupling shaft 26 is held in the support housing 19 both in the axial direction and in the radial direction by the support bearing 22.
  • the coupling shaft 26 has a free protruding from the support housing 19 end, which is coupled with a drive (not shown here).
  • the follower gear 5 is rotatably connected to the circumference of a shaft journal 23 with this.
  • the shaft journal 23 penetrates the bore of the Gear 5 and is held supported on both sides of the gear 5 in Aufhahmebohrept 35 of the housing plate 1.1 and the housing plate 1.2.
  • the bearing means 8.3 and 8.4 are provided on both sides of the gear 5 for this purpose.
  • the bearing means 8.3 and 8.4 are formed by rolling bearings 32, which is identical in construction to the rolling bearings 32 which support the drive shaft 7.
  • each of the bearings 32 has a plurality of rolling elements 30, which are held in a closed annular chamber 31, each with a grease filling.
  • each of the sealing means 9.3 and 9.4 each have a pressure ring 10.3 and 10.4.
  • the pressure rings 10.3 and 10.4 are held by spring means 11.3 and 11.4 under bias on the end faces of the gear 5.
  • each pressure ring 10.3 and 10.4 each have a sealing shoulder 16.3 and 16.4, which are supported on the end faces of the gear 5.
  • the spring means 11.3 and 11.4 are formed in this embodiment by partial spring spring packs, which are fixed in the receiving bore 35 by retaining rings 17.
  • the sealing rings 12.3 and 12.4 are respectively assigned to the bearing means 8.3 and 8.4 at the circumference of the shaft journal 23, the sealing rings 12.3 and 12.4 being formed as groove rings, which form the annular space between the shaft journal 23 and the receiving bore 35 seal to the outside.
  • a washing compartment 13.3 and 13.4 is formed in each case on the circumference of the shaft journal 23.
  • the rinsing chambers 13.3 and 13.4 are in each case by a flushing passage 14.3 in the housing plate 1.1 and a flushing passage 14.4 in the housing plate 1.2 with a flushing port 15.3 the housing plate 1.1 and a flushing port 15.4 connected to the housing plate 1.2.
  • the receiving bore 35 is closed in the housing plate 1.1 and in the housing plate 1.2 each outwardly by a cover 27.
  • the follower gear 5 is also between two pressure rings 10.3 and 10.4 tensioned, wherein the pressure rings 10.3 and 10.4 are also preferably formed of a ceramic material and wherein at least the frontal region of the gear 5, against which the sealing shoulders 16.3 and 16.4 bear with bias, are also formed of a ceramic material.
  • the gears 4 and 5 made of a full ceramic or ceramic-coated side edges.
  • FIGS. 1 to 4 are exemplary in construction and arrangement of the bearing means for supporting the drive shaft and the shaft journal.
  • the rolling bearings can alternatively be replaced by plain bearings or other common storage means.
  • the rinsing channels and flushing connections shown are optional. So rinses on the gear pumps can also be performed on the existing pump connections and the existing gaps between shafts, gears and housing parts. In that case, no additional purge channels would be required. LIST OF REFERENCE NUMBERS

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

Abstract

L'invention concerne une pompe à engrenage, à deux roues dentées mutuellement en prise (4, 5) comprenant une roue dentée entraînée (4) et une roue dentée menée (5). Il est prévu, pour la commande de la roue dentée, un arbre de commande (7) monté rotatif, qui est maintenu par un palier (8.2) dans le carter de la pompe (1). Un agent d'étanchéité (9.2), associé à l'arbre de commande (7), à la périphérie entre la roue dentée et le palier, comprend une bague de pression (10.2) s'appliquant sur une face frontale de la roue dentée. En vue d'empêcher une mise en marche de la roue dentée dans le carter de la pompe, l'invention est caractérisée en ce qu'un second agent d'étanchéité (9.1) ayant une seconde bague de pression (10.1) sur la face frontale opposée de la roue dentée (4) est disposé sur la périphérie de l'arbre moteur (7) entre un second palier (8.1) et la roue dentée (4), et en ce que les deux bagues de pression (10.1, 10.2) présentent, vis-à-vis de la roue dentée (4), respectivement, un épaulement d'étanchéité (16.1, 16.2) qui est sollicité par un moyen à ressort s'appliquant par pression sur la face frontale de ladite roue dentée.
PCT/EP2008/053968 2007-05-03 2008-04-02 Pompe à engrenage Ceased WO2008135326A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
DE502008001091T DE502008001091D1 (de) 2007-05-03 2008-04-02 Zahnradpumpe
AT08735717T ATE476600T1 (de) 2007-05-03 2008-04-02 Zahnradpumpe
US12/598,322 US20100196186A1 (en) 2007-05-03 2008-04-02 Gear pump
EP08735717A EP2140142B1 (fr) 2007-05-03 2008-04-02 Pompe à engrenage

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007020703 2007-05-03
DE102007020703.6 2007-05-03

Publications (1)

Publication Number Publication Date
WO2008135326A1 true WO2008135326A1 (fr) 2008-11-13

Family

ID=39665991

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2008/053968 Ceased WO2008135326A1 (fr) 2007-05-03 2008-04-02 Pompe à engrenage

Country Status (6)

Country Link
US (1) US20100196186A1 (fr)
EP (1) EP2140142B1 (fr)
AT (1) ATE476600T1 (fr)
DE (1) DE502008001091D1 (fr)
ES (1) ES2349495T3 (fr)
WO (1) WO2008135326A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010132154A2 (fr) 2009-05-12 2010-11-18 Illinois Tool Works Inc. Système d'étanchéité pour pompes à engrenages
CN104554224A (zh) * 2013-10-09 2015-04-29 株式会社电装 具有密封机构的旋转泵送装置
WO2018153605A1 (fr) * 2017-02-24 2018-08-30 Robert Bosch Gmbh Pompe à engrenage pour un système de récupération de chaleur
EP3364034A4 (fr) * 2015-11-05 2019-06-26 Sumitomo Rubber Industries, Ltd. Dispositif de pompe à engrenages pour extrusion de caoutchouc
DE102021004717A1 (de) 2021-09-20 2023-03-23 Oerlikon Textile Gmbh & Co. Kg Dosierpumpe zum Fördern von abrasiven Fluiden

Families Citing this family (3)

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JP5369068B2 (ja) * 2010-08-27 2013-12-18 日立オートモティブシステムズ株式会社 ポンプ装置
JP2015010499A (ja) * 2013-06-27 2015-01-19 旭サナック株式会社 ギヤポンプ
DE102019102073A1 (de) 2019-01-28 2020-07-30 Fresenius Medical Care Deutschland Gmbh Zahnradpumpe

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EP1280996B1 (fr) * 2000-05-08 2004-03-31 Pomtava Sa Pompe de dosage pour produits liquides
DE102005016670A1 (de) * 2005-04-12 2006-10-19 LacTec Gesellschaft für moderne Lackiertechnik mbH Lackdosierpumpe

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US6183231B1 (en) * 1997-01-31 2001-02-06 United Dominion Industries, Inc. Clean-in-place gear pump
EP1280996B1 (fr) * 2000-05-08 2004-03-31 Pomtava Sa Pompe de dosage pour produits liquides
DE102005016670A1 (de) * 2005-04-12 2006-10-19 LacTec Gesellschaft für moderne Lackiertechnik mbH Lackdosierpumpe

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010132154A2 (fr) 2009-05-12 2010-11-18 Illinois Tool Works Inc. Système d'étanchéité pour pompes à engrenages
WO2010132154A3 (fr) * 2009-05-12 2011-05-12 Illinois Tool Works Inc. Système d'étanchéité pour pompes à engrenages
US8225968B2 (en) 2009-05-12 2012-07-24 Illinois Tool Works Inc. Seal system for gear pumps
CN104554224A (zh) * 2013-10-09 2015-04-29 株式会社电装 具有密封机构的旋转泵送装置
CN104554224B (zh) * 2013-10-09 2017-08-11 株式会社爱德克斯 旋转泵送装置和使用该旋转泵送装置的车辆用制动系统
EP3364034A4 (fr) * 2015-11-05 2019-06-26 Sumitomo Rubber Industries, Ltd. Dispositif de pompe à engrenages pour extrusion de caoutchouc
US10738776B2 (en) 2015-11-05 2020-08-11 Sumitomo Rubber Industries, Ltd. Gear pump device for rubber extrusion
WO2018153605A1 (fr) * 2017-02-24 2018-08-30 Robert Bosch Gmbh Pompe à engrenage pour un système de récupération de chaleur
DE102021004717A1 (de) 2021-09-20 2023-03-23 Oerlikon Textile Gmbh & Co. Kg Dosierpumpe zum Fördern von abrasiven Fluiden

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ATE476600T1 (de) 2010-08-15
DE502008001091D1 (de) 2010-09-16
US20100196186A1 (en) 2010-08-05
ES2349495T3 (es) 2011-01-04
EP2140142B1 (fr) 2010-08-04
EP2140142A1 (fr) 2010-01-06

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