EP0866224A1 - Pompe à engrenages pour le déplacement de fluides - Google Patents

Pompe à engrenages pour le déplacement de fluides Download PDF

Info

Publication number
EP0866224A1
EP0866224A1 EP98103651A EP98103651A EP0866224A1 EP 0866224 A1 EP0866224 A1 EP 0866224A1 EP 98103651 A EP98103651 A EP 98103651A EP 98103651 A EP98103651 A EP 98103651A EP 0866224 A1 EP0866224 A1 EP 0866224A1
Authority
EP
European Patent Office
Prior art keywords
working chamber
gear
gear pump
pump according
parts
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
EP98103651A
Other languages
German (de)
English (en)
Other versions
EP0866224B1 (fr
Inventor
Eugen Dr. Schmidt
Herbert Dr. Schmidt
Walter Dr.-Ing. Thiele
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.)
SGL Carbon SE
Nidec GPM GmbH
Original Assignee
SGL Carbon SE
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=7823494&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0866224(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by SGL Carbon SE, Geraete und Pumpenbau GmbH Dr Eugen Schmidt filed Critical SGL Carbon SE
Publication of EP0866224A1 publication Critical patent/EP0866224A1/fr
Application granted granted Critical
Publication of EP0866224B1 publication Critical patent/EP0866224B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • 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
    • F04C2/082—Details specially related to intermeshing engagement type 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
    • 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
    • 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
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F04C2240/802—Liners
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2203/00—Non-metallic inorganic materials
    • F05C2203/08—Ceramics; Oxides
    • F05C2203/0865—Oxide ceramics
    • F05C2203/0882—Carbon, e.g. graphite

Definitions

  • the invention relates to a gear pump for conveying Fluids according to the preamble of claim 1.
  • Gear pumps with internal teeth and those with external teeth are used to a considerable extent in technology hydraulic power transmission in the pressure range of approx. 10 to 250 bar used.
  • Conveying lubricating fluids such as oils of all kinds Type or of diesel fuel.
  • Conveying lubricating fluids such as oils of all kinds Type or of diesel fuel.
  • poorly or non-lubricating fluids such as Water, low boiling hydrocarbons, in particular Petrol or kerosene, or from solutions or mixtures existing drinks occur when using gear pumps even at low fluid pressures on the outlet side problems from about 2 to 10 bar after a short time.
  • the Friction becomes too high and the pumps fall due to erosion and / or corrosion. Problems of this kind also result in Operating areas in which with a temporary dry run or worked with temporarily interrupted lubricating films must be to the failure of the pumps.
  • Parts made of carbon have long been used in mechanical engineering e.g. as slip rings, sealing rings, slide bearings, slide rings or slide gate (see e.g. Jörres, engineering materials I No. 11/12 (1989) and engineering materials 2, No. 1/2 (1990)).
  • the use of such Parts made of carbon - the following should, if on corresponding differences in material qualities not specifically pointed out in the term Carbon also included graphite - not unproblematic as it is when using carbon parts always choosing one for the prevailing Suitable material pairing for operating conditions arrives.
  • Gear pumps used for pumping fluids missing or insufficient lubricity are, because up to now corresponding attempts at Conveying such media with gear pumps early erosion and / or corrosion-related Failure of the pumps failed.
  • the promotion of fluids of the above type with gear pumps is not technically manageable. It’s therefore a result of inventive rank, if only for promoting such bad or suitable for non-lubricating fluids in continuous operation Gear pumps are provided.
  • An essential feature of the pumps is that they are the most promotional gears surrounding housing of the working chamber the pump made of a synthetically manufactured carbon material exists, which is fluid-tight.
  • the pump made of a synthetically manufactured carbon material exists, which is fluid-tight.
  • both gear wheels located in the delivery chamber axially on the surrounding them on both sides, from the Carbon material existing walls of the delivery chamber slidably mounted.
  • the two sides of the working chamber also as bearing blocks trained for the axes of the gears, so that also the axes of the gears in suitably shaped Bearing bushes made of carbon are stored.
  • the housing of the working chamber preferably consists of a carbon material with a matrix of a carbonized carbon which has not been heated to the graphitization temperature.
  • This matrix is obtained by coking or carbonizing the binder of a precursor body containing coking materials for the production of the carbon material.
  • the pre-product body is composed of the binder and certain fillers. When carbonizing this body, work must be carried out below a temperature at which graphitization processes occur. A final temperature of 900 to 1000 ° C. is preferably used. Coking or carbonization is carried out in the manner known to those skilled in the field of carbon technology with the exclusion of substances having an oxidizing effect.
  • the binder used is either a coal tar pitch, a petroleum pitch or a mixture of one of the aforementioned types of pitch and a synthetic resin.
  • care must be taken to ensure that after carbonization the binder has a coke yield of at least 50, preferably more than 60 and particularly preferably more than 65 percent by weight (determination according to DIN 51905).
  • the binder is mixed with the filler.
  • the binder can be mixed with the filler in both liquid and finely powdered form. Mixing in finely powdered form is used especially when processing pitches with high softening points. However, it is also possible to mix the binder in liquid form with the filler at temperatures above its softening point.
  • carbon moldings can be pressed from mixtures produced by both mixing processes.
  • the preferred procedure when working with pitches is the introduction and mixing in of the binder in powdered form and the subsequent pressing of shaped bodies from the filler powder / binder powder mixture obtained. If a mixture of a binder in liquid form with the filler has been chosen, it is advantageous to grind the binder-filler mixture obtained into a fine particle size before compression to form shaped bodies and then to compress this ground material into shaped bodies.
  • the pressing is preferably carried out in die or isostatic presses. All of the so-called green moldings produced by one of the aforementioned processes are then fed to the carbonization process.
  • the filler content in the preliminary product and in the carbon material consists of 35 to 97% by weight of graphite, 0 to 62% by weight of non-graphitized petroleum or hard coal tar pitch coke and 3 to 20% by weight of mineral, the tribological properties of the components influencing the material.
  • the graphitic part of the filler can be natural graphite, kishgraphite, electrographite, ie graphite produced synthetically, electrothermally or also graphitized coke, or it can consist of a mixture of one or more of the aforementioned substances.
  • the material in the graphitizing process which must also be carried out with the exclusion of oxidizing media, must be exposed to a temperature of at least 1800 ° C., preferably of more than 2400 ° C. to 3000 ° C.
  • the second part of the filler consists of non-graphitized petroleum or coal tar pitch coke. These cokes already belong to the harder part of the carbon material which has less lubricity but which increases the resistance to abrasion.
  • the third part of the filler is formed by hard materials, which preferably consist of or contain oxides, carbides, nitrides, borides or silicates.
  • Silicon dioxide, silicon carbide, aluminum oxide, boron carbide, silicon nitride or feldspar are particularly preferably used.
  • the purpose of these materials is to further increase the abrasion resistance of the carbon material and to keep the counter surfaces clean during operation by means of a slight sanding effect.
  • each of the constituents that later form the filler is ground to a fineness of flour.
  • the moldings produced are after firing the exit of pyrolysis products of the binder fraction porous.
  • a liquid impregnating agent that either solidifies after impregnation, or is cured.
  • Impregnation agents become thermosetting and thermoplastic Resins used.
  • resins from the group of phenolic resins, in particular the Resol types, furan or polyester resins, perfluorinated Hydrocarbon resins or polyamide resins.
  • synthetic resins as impregnating agents must be observed that the operating temperature of the pump by the respective Heat resistance of the impregnating agent is limited.
  • Carbon parts for pumps operating at very high temperatures are to be operated with liquid metals or their alloys such as copper and Copper alloys or antimony and antimony alloys impregnated.
  • the carbon parts can meet the highest demands also by a so-called, the specialist known chemical vapor impregnation (CVI) fluid-tight be made.
  • CVI chemical vapor impregnation
  • gaseous substances in the pore system of the carbon parts introduced the carbon during thermal decomposition or form other hard materials. With this thermal At least the pore entrances are completely decomposed filled with carbon or one of the hard materials what tightness of the body.
  • the gears meshing with each other in the delivery chamber or the working area of the pump can consist of different materials depending on the design, mechanical or thermal load or the medium to be delivered.
  • Stainless steel or a non-ferrous metal is preferably used for the conveyance of water, the parts preferably being produced by a powder metallurgical process.
  • parts made from solid metal pieces or full pieces from a metal alloy can also be used, the manufacture of which, however, is more complex and which have practically no pores. If the requirements regarding the corrosion resistance in the range of comparatively low temperatures are not too high, the parts can consist of thermosetting or thermoplastic plastics such as, for example, hardened phenolic, furan or polyester resins, or polyamides, polyimides.
  • thermosets and thermoplastics are frequently used advantageously in molds equipped with powder and / or fibrous fillers.
  • the specialist uses the known specialist knowledge.
  • gearwheels made of technical ceramics such as porcelain or silicon carbide or, in particular, synthetically produced carbon qualities suitable for use as slide ring or bearing material are used.
  • the carbon bodies can be impregnated or coated with a hard material such as SiC, TiC, WC by one of the methods known from the prior art, for example CVI, CVD (Chemical Vapor Deposition), CVR (Chemical Vapor Reaction) , TiB 2 , Si 3 N 4 , BC.
  • a hard material such as SiC, TiC, WC by one of the methods known from the prior art, for example CVI, CVD (Chemical Vapor Deposition), CVR (Chemical Vapor Reaction) , TiB 2 , Si 3 N 4 , BC.
  • the housing of the pump which delimits the working chamber of the Pump made of the carbon material can be used accordingly more stable, i.e. thick-walled version also without others this case supportive and protective cover get along.
  • the housing is made of the carbon material from a mechanically supporting internal pressure force absorbing and against mechanical damage like shocks or bumps surrounding the protective sheath.
  • This Shell can be made of a metallic material, a plastic or a material reinforced with fibers. She is trained according to known rules of technology.
  • One of the preferred embodiments of the invention Pumps are internal gear pumps where two are in the Working chamber of the pump gears arranged one inside the other, of which the inner is driven, in one Rotate way that when meshing the external teeth of the inner gear with those on the inside of the outer, ring-shaped gear teeth on the suction side the pump is constantly creating new delivery rooms penetrate into the fluids to be pumped and on the Pressure side of the pump these delivery rooms continuously be reduced again to a minimum value, whereby the fluids located in the production rooms in the Pressure channel are ejected.
  • Prerequisite for functionality such a pump is that the inner Gear a smaller number of teeth than the external gear Has.
  • the housing of the working chamber of the pump consists of two parts which are connected to one another in a fluid-tight manner.
  • the first part has the shape of a pot with a bottom and a cylindrical wall.
  • the second part completely covers the interior of the first part, whereby it has a fluid-tight connection with the upper part of the cylindrical wall of the first part. It preferably lies on the upper, free edge of the wall of the first part in a fluid-tight manner.
  • the lidded pot lying on its outer surface.
  • the gears of the conveyor are mounted within the chamber formed from the pot and the lid, with all the walls of the carbon material delimiting the chamber simultaneously being the bearings. The following different positions result.
  • the outer circumferential surface of the outer gearwheel viewed in the radial direction, is mounted on the inner wall of the cylindrical jacket-shaped wall of the pot and is unrolled there when the pump is in operation, and on the other hand, both sides of the two gearwheels are on the side walls of the working chamber, i.e. once on the floor of the pot and the other on the inside of the lid in a sliding and sealed manner.
  • the suction and pressure-side recesses in the side walls of the working chamber which are matched to the delivery spaces in the gearwheels of the pump and which are connected to the corresponding suction and pressure channels, can be used in one of the two side parts delimiting the working chamber (bottom of the pot or lid).
  • the side part, in which these recesses are located with their channel connections, must then be made so thick that these functional elements of the pump have space therein.
  • These recesses are preferably accommodated in the side part of the work space facing away from the drive of the pump. However, it is also possible to arrange these functional elements on the drive side or to arrange the recesses on both sides of the working chamber.
  • the storage of the gears and the drive of the Internal gear corresponds to that of a pump two-part housing with the difference that that is in the bottom of the pot in the two-part design arranged bearings now through the camp in a block or plate-shaped Sidewall is replaced. How the This will not pump or store the gears changed.
  • the inner gearwheel of the internal gearwheel pump preferably has a shaft which is arranged centrally on one of its flat sides and which, on this side, is sealed out through the housing of the working chamber and is connected to a drive there.
  • a shaft which is arranged centrally on one of its flat sides and which, on this side, is sealed out through the housing of the working chamber and is connected to a drive there.
  • a further improvement in the guidance of the gears of an internal gear pump is achieved in that on one or both of the flat sides of the driven gear there is a cylindrical elevation which is arranged concentrically around its shaft and is fixedly connected to the gear, and which is in a complementary hollow cylindrical recess in the adjacent inner wall the working chamber fits and is rotatably mounted there and with low tolerance.
  • the shaft only extends to one side of the gearwheel, such cylindrical elevations with their complementary bearings can nevertheless be located in the adjacent side wall of the working chamber on its two sides.
  • the cylindrical elevation can also be designed in the form of a cylinder jacket arranged concentrically around the shaft, the radially outer jacket surface of which is the running surface sliding in the bearing.
  • the version with an additional bearing arranged only on one of the flat sides is preferably used.
  • gear pumps of this invention are external gear pumps.
  • two gearwheels, each with external toothing are arranged next to one another in a working chamber, and the teeth of these gearwheels mesh with one another, sealing the suction of the pressure chamber of the pump, the fluid between the suction in the interdental spaces of the teeth that are not in meshing engagement - conveyed to the pressure side and is expelled on the pressure side by the pressure built up by the conveyance.
  • at least the walls of the working chamber consist of a carbon material and the gearwheels are mounted in multiple ways on and in the walls delimiting the working chamber.
  • the axially arranged sides of the gears slide sealingly on the side walls of the working chamber
  • the outer radial flanks of the teeth of the gears slide along their entire width sealingly on the inner wall of the envelope part delimiting the working space in the radial direction
  • the shafts of the gears in bearing blocks made of carbon which are located in the side parts of the working chamber forming the carbon material.
  • the housing of the working chamber of such an external gear pump preferably consists of three parts.
  • the pumps according to the invention are preferably used for the Promotion of liquids of the aforementioned type with Pressure on the pressure side of 2 bar and more, especially preferably used from 3 to 8 bar.
  • the filler and pitch binder were then mixed intimately at room temperature in a high-speed mixer. After it had been discharged from the mixer, the finely powdered mixture was poured into the mold of a die press and pressed there without extraneous heating under a pressure of 200 MPa to give a shaped body. If the somewhat difficult handling of the fine powder mixture is to be avoided, after thorough mixing of the powder filler with the powder binder, the mixture can be heated to a product temperature of approx. 150 ° C with further mixing. After discharging from the mixer and cooling the mixture, it must then be broken or ground to a fineness with a maximum grain size of 1 mm.
  • the lump grind obtained in this way is then pressed into shaped bodies as described above.
  • the moldings were then heated in a ring furnace with a firing regime for fine-grained carbon material to a final temperature of 1200 ° C., whereby the binder was carbonized and a porous, solid carbon body was obtained.
  • This body was then impregnated with a phenol resole type impregnating resin to make it fluid-tight by the vacuum pressure method.
  • the parts required for the housing of a gear pump were then machined from the impregnated blank made of the carbon material.
  • the fluid-tight carbon material had the following physical data: Hardness HRB 10/100 (DIN 51917) 100 Bulk density (DIN IEC 413) 1.83 g / cm 3 Flexural strength (DIN 51902) 55 MPa E-module (DIN 51915) 20 GPa
  • An internal gear pump according to the invention the gears made of powder-metallurgically manufactured stainless steel (material no. Sint C 40, DIN 30910) and the walls the working chamber consisted of a carbon material, the preparation of which has been described in Example 1, was used with water as the medium to be pumped Speed of 3000 / min with a delivery rate of 6 l / min Operated continuously for 30 days without disruptions. After none of those in the working chamber showed this endurance test parts present any erosion or Signs of corrosion. The sliding and bearing surfaces were in excellent condition.
  • FIG. 1 through an internal gear pump shows the cast metal housing of the pump (1), which surrounds the casing of the housing (2) made of carbon of the working chamber (3) in a protective and supportive manner, seen from the outside inwards.
  • the bearing zone (4) shown here as too large a gap between the housing made of the carbon material (2) and the radially outer running surface (5) of the external gear (6).
  • the external gear (6) has an internal toothing (7) which has one tooth more than the external toothing (8) of the internal gear (9) running in it.
  • the internal gear (9) is driven by a shaft (10) arranged eccentrically in the pump housing.
  • the external gear (6) is arranged centrally in the working chamber (3).
  • the internal gear (9) On the side of the shaft (10), the internal gear (9) has a concentric cylindrical elevation (17) which is mounted in the additional bearing (18) shown in FIG. 3, which serves to increase the smooth running of the pump.
  • Figure 2 shows a cross section through a block of a Carbon material that is one of the side walls of the Working chamber (3) forms.
  • the block is from one again Housing (1) made of cast metal, in which the Intake (16) and the pressure channel (15) of the pump are molded are.
  • the intake duct (16) is called the “suction kidney” Recess (12) in the side wall of the working chamber (3) and the pressure channel (15) with the recess called “pressure kidney” (14) connected in the side wall of the working chamber (3).
  • the gears rotating in the working chamber (3) (6) and (9) are on the surface of the side wall forming blocks of carbon shown here slidably mounted and the external gear (6) slides as in Fig. 1 reproduced, in addition with its outer Tread (5) on the inner wall of the casing of the housing from carbon (2) of the working chamber (3) as another Camp.
  • Figure 3 shows a cross section through the working chamber (3) an internal gear pump parallel to the direction the shaft (10) of the internal gear (9).
  • the internal gear (9) has a cylindrical one arranged concentrically around its shaft (10) Elevation (17) with a radial bearing surface (22), in a complementary counter bearing surface (23), which in the bottom of the cup-shaped part of the housing (19) located, fitted and runs in this.
  • Figures 4 and 5 show two cross sections through an external gear pump, one of which is parallel to the shafts (24, 24 ') of the gears (25, 25') (Fig. 4) and the other perpendicular to the shafts (24,24 ' ) of the gears (25, 25 ') (Fig. 5) is guided.
  • the liquid to be conveyed on the suction side (26) enters the pump driven by one of the shafts (24, 24 ') of the gear wheels (25, 25'), enclosed in the interdental spaces (27) of the counter-rotating gears (25, 25 ') are conveyed into the pressure chamber (28) of the pump and ejected from there from the pump.
  • the suction (26) and pressure chamber (28) of the pump are separated from each other by the closely meshing teeth of the gear wheels (25, 25 ').
  • the working chamber (3) of the pump is surrounded by a housing made of a carbon material (2) that slides and seals on the tip circle diameter (29) and the side surfaces (30) of the gear wheels (25, 25 ').
  • the various carbon parts forming the walls of the working chamber (3) and their function can be clearly seen in FIG.
  • the side walls form the blocks 31 and 31 ', which also contain the bearings (32, 32', 32 '', 32 ''') for the shafts (24,24') of the gear wheels (25,25 ').
  • the sides of the blocks (31, 31 ') facing the working chamber (3) form the sealing slide bearings for the side surfaces (30) of the gear wheels (25, 25').
  • the working chamber (3) is completely surrounded by a jacket made of carbon (2), which lies sealingly and slidingly along the conveying zones (27) formed by the teeth on the tip circle diameter (29) of the gear wheels (25, 25 ').
  • This jacket also has the openings for the suction (26) and the pressure channel (28) of the pump.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
EP98103651A 1997-03-17 1998-03-03 Pompe à engrenages pour le déplacement de fluides Expired - Lifetime EP0866224B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19710804 1997-03-17
DE19710804A DE19710804A1 (de) 1997-03-17 1997-03-17 Zahnradpumpe zum Fördern von Fluiden

Publications (2)

Publication Number Publication Date
EP0866224A1 true EP0866224A1 (fr) 1998-09-23
EP0866224B1 EP0866224B1 (fr) 2001-10-04

Family

ID=7823494

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98103651A Expired - Lifetime EP0866224B1 (fr) 1997-03-17 1998-03-03 Pompe à engrenages pour le déplacement de fluides

Country Status (7)

Country Link
US (1) US6053718A (fr)
EP (1) EP0866224B1 (fr)
JP (1) JPH10259785A (fr)
KR (1) KR19980080338A (fr)
DE (2) DE19710804A1 (fr)
DK (1) DK0866224T3 (fr)
ES (1) ES2163816T3 (fr)

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6612821B1 (en) 2000-07-14 2003-09-02 Fluid Management, Inc. Pump, in particular gear pump including ceramic gears and seal
RU2278300C1 (ru) * 2005-06-01 2006-06-20 ООО "Научно-производственное объединение "Орион ВДМ" Шестеренный насос
RU2307260C1 (ru) * 2006-06-09 2007-09-27 ООО "Рос ДМ" Шестеренный дозирующий насос
RU2314435C1 (ru) * 2006-11-15 2008-01-10 ООО "Научно-производственное объединение "Орион ВДМ" Шестеренный насос-дозатор
EP2208889A1 (fr) * 2009-01-20 2010-07-21 BSH Bosch und Siemens Hausgeräte GmbH Appareil de boisson
WO2010133390A3 (fr) * 2009-05-22 2012-03-15 Robert Bosch Gmbh Carter de pompe d'un modulateur hydraulique pour véhicule à moteur
US8951027B2 (en) 2011-10-25 2015-02-10 Danfoss A/S Vane cell machine
US9279424B2 (en) 2011-10-25 2016-03-08 Danfoss A/S Vane cell machine having plates containing axial moving inserts bearing against the rotor
EP4166751A1 (fr) * 2021-10-15 2023-04-19 Atlas Copco Airpower N.V. Compresseur non lubrifié doté d'un élément d'étanchéité abrasible et procédé d'assemblage associé

Families Citing this family (26)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19825376C2 (de) * 1998-06-06 2003-12-11 Bosch Gmbh Robert Zahnradmaschine
DE19826367C2 (de) * 1998-06-12 2000-05-18 Geraete & Pumpenbau Gmbh Innenzahnradpumpe
DE10019516A1 (de) * 2000-04-20 2001-10-31 Hoehn Bernd Robert Zahnräder aus korrosionsbeständigen Stahl
ATE348956T1 (de) * 2001-01-22 2007-01-15 Hnp Mikrosysteme Gmbh Präzise kleinstlagerung und montageverfahren dafür
DE10114148C1 (de) * 2001-03-22 2002-06-06 Dieter Brox Selbstzentrierende Zahnradpumpe
DE10128055C2 (de) * 2001-06-01 2003-09-25 Sgl Carbon Ag Gleitpaarung für von Wasserdampf mit hohem Druck-und Temperaturniveau beaufschlagte Maschinenteile, vorzugsweise für Kolben-Zylinder-Anordnungen von Dampfmotoren
US6592348B1 (en) * 2002-03-27 2003-07-15 Production Research, Inc Lubricant pump and method of producing
US6997689B2 (en) * 2003-02-20 2006-02-14 Honeywell International Inc. Offset bearing for extended fuel pump life
DE10327321A1 (de) * 2003-06-16 2005-01-13 Siemens Ag Als G-Rotorpumpe ausgebildete Verdrängerpumpe
KR20050093981A (ko) * 2004-03-17 2005-09-26 민경은 열경화성 수지를 이용한 미케니컬 씰의 조성물 및 그의제조방법
WO2006015218A1 (fr) * 2004-07-30 2006-02-09 Pulsafeeder, Inc. Pompe à engrenages non métallique avec ensemble d'accouplement magnétique
US7220111B2 (en) * 2004-08-02 2007-05-22 Production Research, Llc Hydraulic pump
US7017340B2 (en) * 2004-08-18 2006-03-28 Ford Global Technologies, Llc Hydrokinetic torque converter for an automatic vehicle transmission
US20060047065A1 (en) * 2004-08-30 2006-03-02 Wiebke Becker Aqueous coating compositions based on acrylate copolymers
ES2378989T3 (es) * 2004-10-27 2012-04-19 Sgl Carbon Se Cuerpo de material deslizante resistente al desgaste de grafito y aglutinante de resina sintética
RU2493751C2 (ru) * 2008-04-09 2013-09-27 Нестек С.А. Шестеренные насосы и способы их использования
JP4977112B2 (ja) * 2008-11-17 2012-07-18 日立オートモティブシステムズ株式会社 ギヤポンプ
US8840385B2 (en) 2011-03-03 2014-09-23 Ti Group Automotive Systems, L.L.C. Positive displacement fluid pump
JP2012202254A (ja) * 2011-03-24 2012-10-22 Hitachi Automotive Systems Ltd ポンプ装置
CN102678541B (zh) * 2012-05-25 2014-08-06 山东鑫亚工业股份有限公司 悬浮式摆线转子输油泵
DE102013201384A1 (de) * 2013-01-29 2014-07-31 Robert Bosch Gmbh Innenzahnradpumpe
JP6086239B2 (ja) * 2013-08-09 2017-03-01 アイシン精機株式会社 流体ポンプ用インナロータ
JP2016205170A (ja) * 2015-04-17 2016-12-08 セイコーエプソン株式会社 ギヤポンプおよびこれを備えた印刷装置
DE102015225734A1 (de) 2015-12-17 2017-06-22 Robert Bosch Gmbh Innenzahnradpumpe
KR20180065312A (ko) * 2016-12-07 2018-06-18 엘지전자 주식회사 의류처리장치
DE102021004717A1 (de) * 2021-09-20 2023-03-23 Oerlikon Textile Gmbh & Co. Kg Dosierpumpe zum Fördern von abrasiven Fluiden

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2611323A (en) * 1948-11-30 1952-09-23 Harold D Digney Pump
DE2422783A1 (de) * 1974-05-10 1975-11-27 Siemens Ag Vorrichtung zur foerderung von fluessigen medien, insbesondere zur foerderung von kraftstoffen in kraftfahrzeugen
JPS57148084A (en) * 1981-03-09 1982-09-13 Matsushita Electric Ind Co Ltd Pump device for sprayer

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2619040A (en) * 1949-03-15 1952-11-25 Maisch Oliver Liquid measuring and dispensing pump
GB1236935A (en) * 1967-09-02 1971-06-23 Plessey Co Ltd Improvements in or relating to gear pumps more particularly for use with hot hydrocarbon liquid fuels
DE7802765U1 (de) * 1978-01-31 1979-10-31 Allweiler Ag, 7760 Radolfzell Schraubenspindelmaschine
DE2938276A1 (de) * 1979-09-21 1981-04-09 Robert Bosch Gmbh, 7000 Stuttgart Fluegelzellenverdichter
JPS58220989A (ja) * 1982-06-14 1983-12-22 Diesel Kiki Co Ltd 可変容量式ベ−ン型圧縮機
DE3340748C2 (de) * 1983-11-10 1986-09-25 Fresenius AG, 6380 Bad Homburg Zahnradpumpe, insbesondere für medizinische Zwecke
JPS60204992A (ja) * 1984-03-29 1985-10-16 Diesel Kiki Co Ltd ベ−ン型圧縮機
US4804317A (en) * 1987-03-13 1989-02-14 Eaton Corporation Rotary vane pump with floating rotor side plates
DE4021500C3 (de) * 1990-07-05 1998-10-22 Mannesmann Vdo Ag Förderaggregat, insbesondere zum Fördern von Kraftstoff
US5181844A (en) * 1991-08-15 1993-01-26 Sigma Tek, Inc. Rotary vane pump with carbon/carbon vanes

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2611323A (en) * 1948-11-30 1952-09-23 Harold D Digney Pump
DE2422783A1 (de) * 1974-05-10 1975-11-27 Siemens Ag Vorrichtung zur foerderung von fluessigen medien, insbesondere zur foerderung von kraftstoffen in kraftfahrzeugen
JPS57148084A (en) * 1981-03-09 1982-09-13 Matsushita Electric Ind Co Ltd Pump device for sprayer

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 6, no. 253 (M - 178)<1131> 11 December 1982 (1982-12-11) *

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6612821B1 (en) 2000-07-14 2003-09-02 Fluid Management, Inc. Pump, in particular gear pump including ceramic gears and seal
RU2278300C1 (ru) * 2005-06-01 2006-06-20 ООО "Научно-производственное объединение "Орион ВДМ" Шестеренный насос
RU2307260C1 (ru) * 2006-06-09 2007-09-27 ООО "Рос ДМ" Шестеренный дозирующий насос
RU2314435C1 (ru) * 2006-11-15 2008-01-10 ООО "Научно-производственное объединение "Орион ВДМ" Шестеренный насос-дозатор
EP2208889A1 (fr) * 2009-01-20 2010-07-21 BSH Bosch und Siemens Hausgeräte GmbH Appareil de boisson
WO2010133390A3 (fr) * 2009-05-22 2012-03-15 Robert Bosch Gmbh Carter de pompe d'un modulateur hydraulique pour véhicule à moteur
US8951027B2 (en) 2011-10-25 2015-02-10 Danfoss A/S Vane cell machine
US9279424B2 (en) 2011-10-25 2016-03-08 Danfoss A/S Vane cell machine having plates containing axial moving inserts bearing against the rotor
EP4166751A1 (fr) * 2021-10-15 2023-04-19 Atlas Copco Airpower N.V. Compresseur non lubrifié doté d'un élément d'étanchéité abrasible et procédé d'assemblage associé
WO2023062479A1 (fr) * 2021-10-15 2023-04-20 Atlas Copco Airpower, Naamloze Vennootschap Compresseur non lubrifié doté d'un élément d'étanchéité abradable et son procédé d'assemblage
BE1029799B1 (nl) * 2021-10-15 2023-09-01 Atlas Copco Airpower Nv Niet-gesmeerde compressor met slijtwillig afdichtingselement en verwante werkwijze om deze te monteren
MA65666A1 (fr) * 2021-10-15 2024-07-31 Atlas Copco Airpower, Naamloze Vennootschap Compresseur non lubrifié doté d'un élément d'étanchéité abradable et son procédé d'assemblage
US12345262B2 (en) 2021-10-15 2025-07-01 Atlas Copco Airpower, Naamloze Vennootschap Non-lubricated compressor with abradable sealing element and related method for assembling it

Also Published As

Publication number Publication date
DE59801606D1 (de) 2001-11-08
US6053718A (en) 2000-04-25
DK0866224T3 (da) 2002-01-28
JPH10259785A (ja) 1998-09-29
DE19710804A1 (de) 1998-09-24
EP0866224B1 (fr) 2001-10-04
KR19980080338A (ko) 1998-11-25
ES2163816T3 (es) 2002-02-01

Similar Documents

Publication Publication Date Title
EP0866224B1 (fr) Pompe à engrenages pour le déplacement de fluides
DE10066044B4 (de) Verfahren zum Herstellen eines Reibkörpers aus siliziumfiltriertem, Kohlenstofffaser verstärktem porösen Kohlenstoff und Verwendung eines solchen Reibkörpers
DE68906805T2 (de) Materialverbindung aus flexiblen Graphitteilchen und unkristallisiertem Kohlenstoff.
DE3855544T2 (de) Keramische Verbundwerkstoff und Verfahren zur Herstellung desselben
DE3312868C2 (de) Hydropumpe
EP3380444B1 (fr) Élément en plastique chargé carbone
DE2353551B2 (de) Keramisches Turbinenlaufrad
DE69200935T2 (de) Zahnraddosierpumpe für elastomeres Material.
DE2750137A1 (de) Kreiselpumpe bzw. -verdichter
EP0464261A1 (fr) Pompe d&#39;alimentation en combustible
DE19815989A1 (de) Kolben-Zylinder-Anordnung
EP1337737B1 (fr) Systeme d&#39;association coulissante pour pieces de machine qui sont soumises a l&#39;effet d&#39;une vapeur d&#39;eau a pression et temperature elevees, de preference pour ensembles piston-cylindre de moteurs a vapeur
EP1489331B1 (fr) Corps de friction en carbone poreux renforcé par des fibres et infiltré de métal
DE2362940A1 (de) Dichtungselement fuer den kolben eines verbrennungsmotors
CH646763A5 (de) Wellendichtung fuer hydraulische maschinen.
EP2654935B1 (fr) Mélangeur dynamique
DE3506475C2 (fr)
DE102010055682A1 (de) Gehäuse einer Außenzahnradmaschine und Außenzahnradmaschine
WO2004101836A2 (fr) Pompe a huile
DE10032044B4 (de) Gleitlager mit Festschmierstoff
DE2422783A1 (de) Vorrichtung zur foerderung von fluessigen medien, insbesondere zur foerderung von kraftstoffen in kraftfahrzeugen
EP0717019B1 (fr) Garniture étanche à anneau glissant en carbone
EP0900610B1 (fr) Procédé de préparation de palier en métal fritté pour arbre céramique ainsi que palier obtenu
AT519398A1 (de) Verfahren zur Herstellung einer Taumelscheibe
DE918909C (de) Geschlitzter Kolbenring

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19980717

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): BE CH DE DK ES FR GB IE IT LI NL SE

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

AKX Designation fees paid

Free format text: BE CH DE DK ES FR GB IE IT LI NL SE

RBV Designated contracting states (corrected)

Designated state(s): BE CH DE DK ES FR GB IE IT LI NL SE

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

17Q First examination report despatched

Effective date: 20010226

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): BE CH DE DK ES FR GB IE IT LI NL SE

REG Reference to a national code

Ref country code: CH

Ref legal event code: NV

Representative=s name: PATENTANWAELTE BREITER + WIEDMER AG

Ref country code: CH

Ref legal event code: EP

REF Corresponds to:

Ref document number: 59801606

Country of ref document: DE

Date of ref document: 20011108

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: GERMAN

ET Fr: translation filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20020102

REG Reference to a national code

Ref country code: DK

Ref legal event code: T3

REG Reference to a national code

Ref country code: ES

Ref legal event code: FG2A

Ref document number: 2163816

Country of ref document: ES

Kind code of ref document: T3

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020304

Ref country code: ES

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020304

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020331

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020331

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20020331

PLBQ Unpublished change to opponent data

Free format text: ORIGINAL CODE: EPIDOS OPPO

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

PLBF Reply of patent proprietor to notice(s) of opposition

Free format text: ORIGINAL CODE: EPIDOS OBSO

26 Opposition filed

Opponent name: WILO GMBH

Effective date: 20020702

BERE Be: lapsed

Owner name: *GERATE- UND PUMPENBAU G.M.B.H.

Effective date: 20020331

Owner name: *SGL CARBON A.G.

Effective date: 20020331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20021001

NLR1 Nl: opposition has been filed with the epo

Opponent name: WILO GMBH

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

NLV4 Nl: lapsed or anulled due to non-payment of the annual fee

Effective date: 20021001

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

PLBF Reply of patent proprietor to notice(s) of opposition

Free format text: ORIGINAL CODE: EPIDOS OBSO

PLCK Communication despatched that opposition was rejected

Free format text: ORIGINAL CODE: EPIDOSNREJ1

PLBN Opposition rejected

Free format text: ORIGINAL CODE: 0009273

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: OPPOSITION REJECTED

REG Reference to a national code

Ref country code: ES

Ref legal event code: FD2A

Effective date: 20030410

27O Opposition rejected

Effective date: 20031229

PLAB Opposition data, opponent's data or that of the opponent's representative modified

Free format text: ORIGINAL CODE: 0009299OPPO

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DK

Payment date: 20100310

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20100327

Year of fee payment: 13

Ref country code: FR

Payment date: 20100402

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20100322

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20100312

Year of fee payment: 13

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20110331

Year of fee payment: 14

REG Reference to a national code

Ref country code: DK

Ref legal event code: EBP

REG Reference to a national code

Ref country code: SE

Ref legal event code: EUG

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20110303

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20111130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110331

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110303

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110303

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DK

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110331

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 59801606

Country of ref document: DE

Effective date: 20121002

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110304

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20121002