EP2122175A1 - Pompe à engrenages - Google Patents

Pompe à engrenages

Info

Publication number
EP2122175A1
EP2122175A1 EP08717596A EP08717596A EP2122175A1 EP 2122175 A1 EP2122175 A1 EP 2122175A1 EP 08717596 A EP08717596 A EP 08717596A EP 08717596 A EP08717596 A EP 08717596A EP 2122175 A1 EP2122175 A1 EP 2122175A1
Authority
EP
European Patent Office
Prior art keywords
gear
drive shaft
housing
pump according
gear pump
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
EP08717596A
Other languages
German (de)
English (en)
Other versions
EP2122175B1 (fr
Inventor
Arkadiusz Tomzik
Ulrich Helbing
Dietrich Witzler
Michael Baumann
Frank Herre
Martin Stiegler
Herbert Martin
Thomas Appel
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.)
Duerr Systems AG
Oerlikon Textile GmbH and Co KG
Original Assignee
Duerr Systems AG
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 Duerr Systems AG, Oerlikon Textile GmbH and Co KG filed Critical Duerr Systems AG
Priority to PL08717596T priority Critical patent/PL2122175T3/pl
Publication of EP2122175A1 publication Critical patent/EP2122175A1/fr
Application granted granted Critical
Publication of EP2122175B1 publication Critical patent/EP2122175B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • 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
    • F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
    • F04C13/005—Removing contaminants, deposits or scale from the pump; Cleaning
    • 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
    • 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
    • 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
    • F04C2/086—Carter

Definitions

  • the invention relates to a gear pump, in particular for conveying colored paints according to the preamble of claim 1.
  • a gear pump is known in which the delivery channel system and the scavenger system are connected within the pump housing solely through the gaps between the pump housing, the gears of the drive shaft and the bearing journal.
  • the paint residues that have entered the column can be removed by intensive rinsing.
  • the drive shaft is connected via a press fit with the gear, which, however, makes it difficult to disassemble and assemble easily between the drive shaft and the gear.
  • Another object of the invention is to provide a gear pump of the generic type, in which the assembly and disassembly possible even after longer periods of operation remain.
  • This object is achieved in that the gap between the drive shaft and the gear is sealed by a sealant to the end faces of the gear.
  • the sealant is preferably formed by two spaced-apart sealing rings on the circumference of the drive shaft, wherein the distance between the seal rings is equal to or smaller than that Width of the gear.
  • the gap can be sealed substantially over the full width of the gear so that essentially no or only small transition regions of the gap remain accessible.
  • the sealing surfaces can be both on the circumference of the drive shaft and in bore sections realize the gear.
  • the variant of the invention is preferably used, in which the connecting means is formed by a pin which is fixedly connected to the drive shaft and which engages in a forming groove of the gear. This allows high torques to be transferred safely.
  • the connecting means by a polygonal shape of the drive shaft, which cooperates with a polygonal shape of the bore of the gear.
  • the polygonal shape is preferably introduced in the middle diameter step of the drive shaft or gearwheel bore. This development of the invention is particularly suitable for applying the highest possible torques.
  • connection means with at least one faulty detent which is held on the circumference of the drive shaft
  • a flushing channel system is formed by a plurality of flushing channels, through which the bearing point of the drive shaft can be flushed over its length, in each case from outside to inside.
  • the flushing fluid flowing from the outside inwards thus leads the paint residues back into the interior of the pump in order to flush them outward via the pump inlet or the pump outlet.
  • the pump housing is formed in several parts, wherein the end faces of the gears are held between two housing plates and wherein the drive shaft with at least a shaft portion is rotatably supported directly on the receiving bore of the housing plate.
  • 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.
  • FIG. 2 shows schematically a sectional view of the exemplary embodiment of the inventive gear pump according to FIG. 1
  • Fig. 4 and Fig. 5 schematically shows several sectional views of another exemplary embodiment of the inventive gear pump.
  • Fig. 6 shows schematically a sectional view of another exemplary embodiment of the inventive gear pump
  • 1.1 and 1.2 each have a sealing ring 1.4 and 1.5 are 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 second gear 4 is rotatably connected to a drive shaft 7.
  • the gear 4 is penetrated in a central bore 12 of the drive shaft 7.
  • a connecting means 9 is provided, through which a positive and rotationally fixed connection between the drive shaft 7 and the gear 4 is formed.
  • the connecting means 9 is formed by a detent 10.
  • the catch 10 has, at several points of the circumference of the drive shaft 7, a latching body 10. 1 which is let into a shaft recess 11 and which is tensioned by a spring 10. 2 acting radially outwards.
  • the locking body 10.1 is held by the spring 10.2 in a recess 13 of the bore 12 of the gear 4.
  • the recess 13 in the bore 12 of the gear 4 is adapted to the locking body 10.1, so that upon rotation of the drive shaft 7, the gear 4 is driven.
  • the detent 10 is formed by two offset by 180 ° on the circumference of the drive shaft arranged detent body 10.1.
  • the sealing means are in particular designed such that the connection means 9 provided between the gear 4 and the drive shaft 7 is located in a completely sealed area inside the pump housing 1.
  • the sealing means is formed in this embodiment by two spaced-apart sealing rings 14.1 and 14.2.
  • the sealing rings 14. 1 and 14. 2 are each held in sealing grooves 15. 1 and 15. 2, which are introduced radially in the bore 12 of the gear 4.
  • the sealing grooves 15.1 and 15.2 are the associated with respective end faces of the gear 4, so that the gap formed between the drive shaft 7 and the gear 4 is sealed substantially over its entire width.
  • the sealing rings 14.1 and 14.2 are assigned directly to the end faces of the toothed wheel 4, so that the distance between the sealing rings 14.1 and 14.2 is substantially equal to the width of the gear 4.
  • the inlet 19 opens into a recess of the bearing bag bore 16.
  • the detergent is directly formed by a groove formed as a flushing channel 18.1 to the gap formed in the bearing 8.1 between the drive shaft 7 and the housing plate 1.1 guided.
  • the bearing 8.1 is flowed through from the outside to the inside of the detergent.
  • the second formed in the housing plate 1.2 8.2 bearing is connected via the flushing channels 18.2, 18.3 and 18.4 with the inlet 19.
  • the flushing channels 18.2 and 18.3 are formed as bores within the drive shaft 7 in order to feed the flushing agent into an annular space formed between the shaft sealing ring 20 and the bearing point 8.2.
  • the flushing channels 18.5, 18.6 and 18.7 are formed by bores in the housing plate 1.1 and the bearing pin 21 to connect the gap formed between the gear 5 and the bearing pin 21 with the inlet 19.
  • the flushing channel 18.8 is formed as an axially extending groove in the gear hole of the gear 5, so that the entire bearing area of the gear 5 is flushed through.
  • FIG. 3 shows a further exemplary embodiment of the gear pump according to the invention in a cross-sectional view.
  • the embodiment of FIG. 3 also has a multi-part pump housing 1, which is formed by the housing plates 1.1 and 1.2 and the center plate 1.3 and a seal housing 26.
  • the seal housing 26 is pressure-tightly connected to the housing plate 1.2.
  • the pump inlet 2 is located in the housing plate 1.2 and the pump outlet 3 opposite in the housing.
  • housing plate 1.1 formed.
  • the conveying channel system 6 forming holes in the housing plate 1.2 and 1.1 are introduced.
  • the gears 4 and 5 are held between the housing plates 1.1 and 1.2.
  • the driven gear 4 is coupled directly to the bearing end 7.1 to a drive shaft 7.
  • the drive shaft 7 and the bore 12 of the gear 4 have a plurality of diameter stages 23.1 and 23.2.
  • an axially extending forming groove 25 is provided within the bore 12, in which a pin 24 of the drive shaft 7 engages.
  • the pin 24 is for this purpose firmly connected to the drive shaft 7 and projects beyond the circumference of the diameter step 23.1 addition.
  • the provided in the bore 12 of the gear 4 Formnut 25 and attached to the periphery of the drive shaft 7 pin 24 in this case form the connecting means 9 in order to obtain a non-rotatable positive connection between the drive shaft 7 and the gear 4.
  • sealing rings 14.1 and 14.2 are provided for sealing the gaps formed between the drive shaft 7 and the gear 5.
  • the sealing ring 14.1 is held in this case in the diameter stage 23.1 in a circumferential groove 12 in the bore 15.1.
  • the sealing ring 14.2 is held in the diameter step 23.2 in a sealing groove 15.2 on the circumference of the drive shaft 7.
  • the meshing with the driven gear 4 gear 5 is held on the journal 21.
  • the bearing pin 21 has a smaller width in relation to the gear 5 and is firmly pressed into the bore of the gear 5, so that the gear 5 is guided only by the housing plates 1.1 and 1.2 and by the middle lplatte 1.3 and by the gear 4th is driven.
  • 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 housing plates 1.1 and 1.2 leakage is held by the arranged between the drive shaft 7 and the gear 4 sealant 14.1 and 14.2, so that the gaps between the gear 4th and the drive shaft 7 in particular in the region of the connecting means 9 remains free of leaks.
  • the gear pump shown in Fig. 3 In order to free the column within the pump housing of paint residues during a color change, it is also possible to carry out the gear pump shown in Fig. 3 with a scavenging system.
  • the gap formed in the bearing 8 between the drive shaft 7 and the housing plate 1.2 and the gap formed between the end faces of the gear wheels 4 and 5 and the housing plates 1.1 and 1.2 would be flushed through by a flushing agent.
  • the scavenging system would be connected via a separate inlet and flushing channels with the conveyor channel system.
  • the coupling end 7.2 of the drive shaft 7 projects out of the pump housing 1.
  • the coupling end 7.2 of the drive shaft 7 has in the end region on a diameter shoulder 40 on which a support ring 34 is applied.
  • the support ring 34 is L-shaped and is held in a recess of a support housing 33.
  • the tensioning means 28 is formed by a spring, which is held in the seal housing via a clamping bush 29.
  • annular space 35 is formed between the stuffing box 27 and the shaft seal 39.
  • the annular space 35 is connected via two channels 36. 1 and 36. 2 respectively to an inlet 37 and an outlet 38 in the sealing housing 26.
  • the inlet 37 and the outlet 38 are designed to be closable, so that in the operating state a barrier liquid is introduced into the seal housing 26, through which the annular space 35 is filled.
  • a solvent-containing fluid is used as barrier liquid in order to dissolve the paint particles possibly leaving through gap leaks within the annular space 35, so that hardening in the gap is prevented.
  • the mobility of the gland packing 27 is ensured.
  • a flushing of the annular space 35 via the channels 36.1 and 36.2 can be carried out in a simple manner during maintenance and replacement of the barrier liquid.
  • the scavenging system 18 formed inside the pump housing is identical to the exemplary embodiment according to FIGS. 1 and 2, so that no further explanation is given at this point.
  • the non-sealed gaps between the housing plates 1.1 and 1.2, the drive shaft 7 and the gears 4 and 5 can thus advantageously flush through a detergent.
  • the gears 4 and 5 are held between the housing plates 1.1 and 1.2.
  • the driven gear 4 is connected via a stepped bore 12 with the drive shaft 7.
  • the drive shaft 7 has two diameter stages 23.1 and 23.2. In the transition region of the diameter stages 23.1 and 23.2, an axially extending mold groove 25 is provided within the bore 12, in which purely pin 24 of the drive shaft 7 engages. For a rotationally fixed positive connection between the drive shaft 7 and the gear 4 is formed.
  • a circumferential pass bar 42 is arranged in the central region of the gear 4 and is fitted without play in the bore 12 of the gear 4. In the areas outside the fitting web 42, a small gap is provided between the diameter section of the diameter step 23. 1 and the bore 12 of the gear 4. Likewise, a clearance fit is also formed between the diameter section of the diameter step 23.2 and the bore 12 of the gear 4, so that the gear around the fitting web 42 can execute a pendulum movement in the axial direction. The pendulum movement of the gear 4 is intercepted on both sides of the fitting web 42 by a respective sealing ring 14.1 and 14.2.
  • the drive shaft penetrates the housing plate 1.2 and a pressure-tight manner connected to the housing plate 1.2 seal housing 26, so that a coupling end 7.2 of the drive shaft 7 is cantilevered held for connecting a drive.
  • a seal is provided, for example, as a stuffing box 27, which is arranged on the circumference of the drive shaft 7 and between the grooves of the housing plate 1.2 and the density housing 26 is tensioned.
  • an additional support bearing of the drive shaft 7 is formed.
  • a rolling bearing 41 is disposed between the seal housing 26 and the drive shaft 7.
  • the rolling bearing 4.1 is supported on a shaft shoulder 40 of the drive shaft.
  • the rolling bearing 41 is associated with a shaft sealing ring 39, which is arranged downstream of the first sealing means 27 on the circumference of the drive shaft 7 to the drive side.
  • the embodiment shown in Fig. 6 is thus particularly suitable to absorb external forces acting on the drive shaft 7 forces through the roller bearing 41 immediately outside of the pump housing 1.
  • the driven gear 4 can be guided within the pump housing 1 free of axial forces. Due to the additional pendulum mobility of the gear 4, a wear-gentle guidance of the gear 4 is possible.

Landscapes

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

Abstract

L'invention concerne une pompe à engrenages avec deux roues dentées en engrènement, qui sont montées de façon rotative à l'intérieur d'un carter de pompe au moyen d'un arbre d'entraînement entraîné et d'un tourillon et qui forment un réseau de canaux de transport entre une entrée de pompe et une sortie de pompe. Plusieurs fentes sont formées entre le carter de pompe, les roues dentées, l'arbre d'entraînement et le tourillon, une des fentes entre l'arbre d'entraînement et une des roues dentées contenant un moyen de liaison assurant une liaison solidaire en rotation de l'arbre d'entraînement avec la roue dentée. Pour empêcher la pénétration de fuites vers le moyen de liaison, la fente entre l'arbre d'entraînement et la roue dentée, conformément à l'invention, est rendue étanche en direction des côtés frontaux de la roue dentée à l'aide d'un moyen d'étanchéité.
EP08717596.4A 2007-03-20 2008-03-11 Pompe à engrenages Active EP2122175B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PL08717596T PL2122175T3 (pl) 2007-03-20 2008-03-11 Pompa zębata

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007013161 2007-03-20
PCT/EP2008/052849 WO2008113712A1 (fr) 2007-03-20 2008-03-11 Pompe à engrenages

Publications (2)

Publication Number Publication Date
EP2122175A1 true EP2122175A1 (fr) 2009-11-25
EP2122175B1 EP2122175B1 (fr) 2015-07-29

Family

ID=39432596

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08717596.4A Active EP2122175B1 (fr) 2007-03-20 2008-03-11 Pompe à engrenages

Country Status (12)

Country Link
US (1) US9004890B2 (fr)
EP (1) EP2122175B1 (fr)
KR (1) KR101503088B1 (fr)
CN (1) CN101657643B (fr)
ES (1) ES2550459T3 (fr)
HU (1) HUE025876T2 (fr)
MX (1) MX2009010073A (fr)
PL (1) PL2122175T3 (fr)
PT (1) PT2122175E (fr)
RU (1) RU2435073C2 (fr)
WO (1) WO2008113712A1 (fr)
ZA (1) ZA200905633B (fr)

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DE102008043991A1 (de) * 2008-11-21 2010-05-27 Thielert Aircraft Engines Gmbh Kraftstoffpumpe für Verbrennungsmotoren
DE102010012653A1 (de) 2010-03-25 2011-09-29 Oerlikon Textile Gmbh & Co. Kg Zahnradpumpe
CN101846094B (zh) * 2010-06-03 2012-08-22 蓝星化工有限责任公司 一种磁力离心泵
JP6811091B2 (ja) * 2014-01-03 2021-01-13 コーニンクラケ ダウ エグバート ビー．ブイ． 飲料調製装置用の交換可能な供給パック、配量器、ポンプアセンブリ、および製造方法
KR101698726B1 (ko) * 2016-07-25 2017-01-20 심만섭 로터리 기어펌프
DE102016214762A1 (de) * 2016-08-09 2018-02-15 Robert Bosch Gmbh Außenzahnradmaschine
EP3431202B1 (fr) * 2017-07-20 2020-07-15 Regal Beloit America, Inc. Ensemble arbre de transmission
EP3656530B1 (fr) * 2018-11-21 2022-08-03 Coperion GmbH Dispositif de raccordement destiné à raccorder une machine à vis sans fin à un engrenage et procédé de nettoyage d'un tel dispositif de raccordement
CN110425130A (zh) * 2019-08-09 2019-11-08 天津铭捷智能装备有限公司 一种齿轮泵

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Also Published As

Publication number Publication date
MX2009010073A (es) 2010-01-20
US20100278676A1 (en) 2010-11-04
CN101657643A (zh) 2010-02-24
US9004890B2 (en) 2015-04-14
ZA200905633B (en) 2010-05-26
HUE025876T2 (en) 2016-04-28
RU2435073C2 (ru) 2011-11-27
PT2122175E (pt) 2015-11-12
ES2550459T3 (es) 2015-11-10
PL2122175T3 (pl) 2016-04-29
WO2008113712A1 (fr) 2008-09-25
KR20100015624A (ko) 2010-02-12
CN101657643B (zh) 2012-12-26
EP2122175B1 (fr) 2015-07-29
KR101503088B1 (ko) 2015-03-16
RU2009138374A (ru) 2011-04-27

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