EP2140142B1 - Pompe à engrenage - Google Patents

Pompe à engrenage Download PDF

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Publication number
EP2140142B1
EP2140142B1 EP08735717A EP08735717A EP2140142B1 EP 2140142 B1 EP2140142 B1 EP 2140142B1 EP 08735717 A EP08735717 A EP 08735717A EP 08735717 A EP08735717 A EP 08735717A EP 2140142 B1 EP2140142 B1 EP 2140142B1
Authority
EP
European Patent Office
Prior art keywords
gear
drive shaft
fact
shaft
pump according
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.)
Not-in-force
Application number
EP08735717A
Other languages
German (de)
English (en)
Other versions
EP2140142A1 (fr
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
Publication of EP2140142A1 publication Critical patent/EP2140142A1/fr
Application granted granted Critical
Publication of EP2140142B1 publication Critical patent/EP2140142B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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 out of the EP 1 280 996 B1 known as the closest prior art.
  • 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 associated with a sealing means which seals the bearing means of the drive shaft relative to a pumping space formed on the circumference of the gear.
  • the sealing means on a ceramic ring which is supported under a bias on a front side 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 faces 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 for each end face with the pump housing an equally large sealing gap.
  • 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 the bearing means to Shield both sides of the gear relative to the pressure rings and each define on the circumference of the drive shaft formed between the pressure ring and the sealing ring washing compartment.
  • 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 bearing means can be performed by bushings for sliding bearing of the drive shaft, but in the case of a 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 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 faces of the gear wheels being held between two housing plates.
  • the plate design allows a Feinstbearbeitung of the pump housing, so that a high Planparallclmaschine 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 and Fig. 2 a first embodiment of the gear pump according to the invention is shown in a schematic sectional view.
  • Fig. 2 shows only an enlarged section of the 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 held between the housing plate 1.1 and 1.2 center plate 1.3 consists. In the end faces of the housing plates 1.1 and 1.2 each have a housing seal 1.4 and 1.5 is arranged, through which the gaps between the middle plate 1.3 and the housing plates 1.1 and 1.2 are sealed to the outside.
  • 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 and a bearing means 8.1 and 8.2 arranged in the housing plate 1.1 and the housing plate 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 displaceable on the circumference of the drive shaft 7 and are supported, each with a sealing shoulder 16.1 and 16.2 on the end faces of the gear 4 from.
  • 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.
  • the spring means 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 trained on the opposite side of the gear 4 in the sealing means 9.2 Spülsch 13.2 is connected via a flushing passage 14.2 in the housing plate 1.2 with a flushing port 15.2.
  • 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 receiving bore 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 driven by the drive shaft 7 gear 4 is in engagement with the gear 5, which is held freely rotatably between the housing plates 1.1 and 1.2 in the middle 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.
  • the gear 4 is driven by the drive shaft 7 in promoting a paint color.
  • a paint supplied via the pump inlet 2 is conveyed to the pump outlet 3 under pressure by the meshing gears 4 and 5 in the delivery channel system 6.
  • the leaking from the delivery channel 6 via the gaps between the end faces of the gears 4 and 5 and the Gcphaseuseplatten 1.1 and 1.2 leakage is held at the end faces of the gear 4 under bias pressure rings 10.1 and 10.2, so that the joint gap between the gear 4 and the drive shaft 7 remains substantially free of leaks.
  • a rinsing liquid is introduced into the pump housing via the flushing connections 15.1 and 15.2 and the spaces between the drive shaft 7. den 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.
  • Fig. 3 and Fig. 4 is a further embodiment of the gear pump according to the invention shown schematically in a cross-sectional view.
  • the embodiment is in the construction of the gear pair of the gears 4 and 5 and the pump housing 1 is substantially identical to the embodiment according to Fig. 1 , so that reference is made to the above description at this point and only the differences will be explained.
  • the components with the same functions have been given identical reference numerals. It also provides Fig. 4 only an enlarged view of a section of Fig. 3 so that the following description applies to both figures.
  • the rotatably connected to the gear 4 drive shaft 7 is formed in this embodiment by a bearing shaft 25 and a coupling shaft 26 which are interconnected 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 bearing means 8.1 and 8.2 associated sealing means 9.1 and 9.2 on the circumference of the bearing shaft 25 and the bearing means 8.1 and 8.2 are identical to the previous 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 receiving bores 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 roller 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 Tel-lerfederwovene which are fixed by retaining rings 17 in the receiving bore 35.
  • the sealing rings 12.3 and 12.4 are assigned to the bearing means 8.3 and 8.4 at the periphery of the shaft journal 23, wherein the sealing rings 12.3 and 12.4 are formed as grooved rings, the annular space between the shaft journal 23 and the receiving bore 35 after Seal the outside.
  • a flushing space 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 stretched between two pressure rings 10.3 and 10.4, 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 with bias, also are formed of a ceramic material.
  • the gears 4 and 5 made of a full ceramic or ceramic-coated side edges.
  • FIGS. 1 to 4 illustrated embodiments 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 purge 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.

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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)

Claims (15)

  1. Pompe à engrenage avec deux roues d'engrenage qui sont en engrènement (4, 5) pour convoyer de la laque colorée, les roues d'engrenage étant formées d'une roue d'engrenage (4) entraînée et d'une roue dentée à rotation en ligne (5), avec au moins un arbre d'entraînement (7) supporté de façon rotative qui est relié solidaire en rotation avec la roue d'engrenage entraînée (4) et qui est retenu par des moyens de support (8.2) dans le carter de pompe (1), l'arbre d'entraînement (7) pouvant être couplé avec un entraînement, et un moyen d'étanchéité (9.2) pouvant être associé à l'arbre d'entraînement (7) sur la circonférence entre la roue d'engrenage (4) et le moyen de support (8.2), moyen de support comprenant une bague à pression (10.2) appliquée sur une face frontale de la roue d'engrenage (4), caractérisée en ce qu'un deuxième moyen d'étanchéité (9.1) est agencé avec une deuxième bague à pression (10.1) sur la face frontale opposée de la roue d'engrenage (4) sur la circonférence de l'arbre d'entraînement (7) entre un deuxième moyen de support (8.1) et la roue d'engrenage (4) et en ce que les deux bagues à pression (10.1, 10.2) ont respectivement une épaule d'étanchéité (16.1, 16,2) laquelle sollicitée par respectivement un moyen de ressort (11.1, 11.2), est pressée contre la face frontale de la roue d'engrenage (4).
  2. Pompe à engrenage selon la revendication 1, caractérisée en ce que les moyens d'étanchéité (9.1, 9.2) ont respectivement une bague d'étanchéité (12.1, 12.2) et en ce que les bagues d'étanchéité (12.1, 12.2) protègent les moyens de support (8.1, 8.2) des deux cotés de la roue d'engrenage (4) contre les bagues à pression (10.1, 10.2) et limitent respectivement sur la circonférence de l'arbre d'entraînement (7) une chambre de rinçage (13.1, 13.2) formée entre la bague à pression (10.1, 10.2) et la bague d'étanchéité (12.1, 12.2).
  3. Pompe à engrenage selon la revendication 2, caractérisée en ce que chacune des chambres de rinçage (13.1, 13.2) est reliée à une connexion de rinçage (15.1, 15.2) à l'intermédiaire d'un canal de rinçage (14.1, 14.2) dans le carter de pompe (1).
  4. Pompe à engrenage selon la revendication 2 ou 3, caractérisée en ce qu'à l'intermédiaire d'une pluralité de rainures de rinçage (36.1, 36.2) les deux chambres de rinçage (13.1, 13.2) sont reliées entre l'arbre d'entraînement (7) et les bagues à pression (12.1, 12.2) et entre l'arbre d'entraînement (7) et la roue d'engrenage (4).
  5. Pompe à engrenage selon l'une des revendications 1 à 4, caractérisée en ce que pour supporter l'arbre d'entraînement (7) les moyens de support (8.1, 8.2) sont formés par au moins deux paliers à rouleaux (32), dont les corps de roulement (30) sont maintenus dans une chambre annulaire (31) remplie de lubrifiant.
  6. Pompe à engrenage selon l'une des revendications 1 à 5, caractérisée en ce que la roue dentée à rotation en ligne (5) est assemblée solidaire en rotation avec un tourillon d'arbre (23) qui des deux cotés de la roue dentée (5) est monté par une pluralité de moyens de support (8.3. 8.4) et en ce que des deux cotés de la roue dentée (5) respectivement un moyen d'étanchéité (9.3, 9.4) est agencé sur la circonférence du tourillon d'arbre (23) qui disposent respectivement d'une bague à pression (10.3, 10.4) appliquée contre la face frontale de la roue dentée (5).
  7. Pompe à engrenage selon la revendication 6, caractérisée en ce que les moyens d'étanchéité (9.3, 9.4) ont respectivement une bague d'étanchéité (12.3, 12.4) et en ce que les bagues d'étanchéité (12.3, 12.4) protègent les moyens de support (8.3, 8.4) des deux cotés de la roue dentée (5) contre les bagues à pression (10.3, 10.4) et limitent respectivement sur la circonférence du tourillon d'arbre (23) une chambre de rinçage (13.3, 13.4) formée entre la bague à pression et la bague d'étanchéité (10.3, 10.4).
  8. Pompe à engrenage selon la revendication 7, caractérisée en ce que chacune des chambres de rinçage (13.3, 13.4) est reliée à l'intermédiaire d'un canal de rinçage (14.3, 14.4) dans le carter (1) de pompe à une connexion de rinçage (15.3. 15.4).
  9. Pompe à engrenage selon la revendication 7 ou 8, caractérisée en ce que les deux chambres de rinçage (13.3, 13.4) sont reliées par une pluralité de rainures de rinçage (36.1, 36.2) entre le tourillon d'arbre (23) et les bagues à pression (10.3, 10.4) et entre le tourillon d'arbre (23) et la roue dentée (5).
  10. Pompe à engrenage selon l'une des revendications 6 à 9, caractérisée en ce que les moyens de support (8.3, 8.4) pour supporter le tourillon d'arbre (23) sont formés par au moins deux paliers à roulement (23), dont les corps de roulement (30) sont maintenus dans une chambre annulaire remplie de lubrifiant (31).
  11. Pompe à engrenage selon l'une des revendications précédentes, caractérisée en ce que les bagues à pression (10.1 - 10.4) sont formées en un matériau céramique et en ce que les bagues d'étanchéité (12.1 - 12.4) sont réalisées respectivement en tant qu'un joint en U à lèvres.
  12. Pompe à engrenage selon l'une des revendications précédentes, caractérisée en ce que les moyens de ressort (111.1 - 11.4) pour presser contre les bagues à pression (10.1 - 10.4) sont formés respectivement par un paquet de ressorts à disques.
  13. Pompe à engrenage selon l'une des revendications 1 à 12, caractérisée en ce que les faces frontales des roues d'engrenage (4, 5) sont formées en un matériau céramique.
  14. Pompe à engrenage selon l'une des revendications 1 à 13, caractérisée en ce que l'arbre d'entraînement (7) est formé par un arbre de palier (25) et par un arbre d'embrayage (26) qui est relié avec l'arbre de palier (25) par une connexion rotative détachable (24), en ce que l'arbre de palier (25) est relié à la roue dentée (4) à l'intérieur du carter de pompe (1) et est monté par les moyens de support (8.1, 8.2) et en ce que l'arbre d'embrayage (26) est monté de manière rotative par un palier de support (22) à l'extérieur du carter de pompe (1) dans un boîtier de support (19) et peut être couplé à l'extrémité libre par un entraînement.
  15. Pompe à engrenage selon la revendication 14, caractérisée en ce que le boîtier de support (19) est relié solidement avec le carter de pompe (1) et est pénétré dans un dégagement (21) par l'arbre d'entraînement.
EP08735717A 2007-05-03 2008-04-02 Pompe à engrenage Not-in-force EP2140142B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007020703 2007-05-03
PCT/EP2008/053968 WO2008135326A1 (fr) 2007-05-03 2008-04-02 Pompe à engrenage

Publications (2)

Publication Number Publication Date
EP2140142A1 EP2140142A1 (fr) 2010-01-06
EP2140142B1 true EP2140142B1 (fr) 2010-08-04

Family

ID=39665991

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08735717A Not-in-force EP2140142B1 (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)

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DE102019102073A1 (de) * 2019-01-28 2020-07-30 Fresenius Medical Care Deutschland Gmbh Zahnradpumpe

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US8225968B2 (en) 2009-05-12 2012-07-24 Illinois Tool Works Inc. Seal system for gear pumps
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
JP5987809B2 (ja) * 2013-10-09 2016-09-07 株式会社アドヴィックス 回転式ポンプ装置
JP6616663B2 (ja) * 2015-11-05 2019-12-04 住友ゴム工業株式会社 ゴム押出し用のギアポンプ装置
DE102017203004A1 (de) * 2017-02-24 2018-08-30 Robert Bosch Gmbh Zahnradpumpe für ein Abwärmerückgewinnungssystem
DE102021004717A1 (de) 2021-09-20 2023-03-23 Oerlikon Textile Gmbh & Co. Kg Dosierpumpe zum Fördern von abrasiven Fluiden

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US3170408A (en) * 1960-01-20 1965-02-23 Waterous Co Rotary pumps
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Also Published As

Publication number Publication date
ATE476600T1 (de) 2010-08-15
DE502008001091D1 (de) 2010-09-16
ES2349495T3 (es) 2011-01-04
US20100196186A1 (en) 2010-08-05
EP2140142A1 (fr) 2010-01-06
WO2008135326A1 (fr) 2008-11-13

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