EP2122175B1 - Pompe à engrenages - Google Patents

Pompe à engrenages Download PDF

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Publication number
EP2122175B1
EP2122175B1 EP08717596.4A EP08717596A EP2122175B1 EP 2122175 B1 EP2122175 B1 EP 2122175B1 EP 08717596 A EP08717596 A EP 08717596A EP 2122175 B1 EP2122175 B1 EP 2122175B1
Authority
EP
European Patent Office
Prior art keywords
gear
driveshaft
housing
fact
drive shaft
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.)
Active
Application number
EP08717596.4A
Other languages
German (de)
English (en)
Other versions
EP2122175A1 (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

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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
    • 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 generic gear pump is out of the DE 10 2005 016 670 A1 known.
  • the known gear pump has two meshing gears, which are rotatably mounted within a pump housing by a drive shaft and a bearing pin. Together with a pump inlet and a pump outlet, the gears within the pump housing form a delivery channel system to deliver a colored lake in liquid or powder form.
  • seals are provided between the end faces of the gears and the pump housing.
  • a Spülkanalsystem is formed within the pump housing to flush out in a color change possible paint residues from the gaps between the pump housing, the gears, the drive shaft and the bearing pin.
  • a gear pump is known in which the delivery channel system and the scavenger system within the pump housing are connected solely by the gaps between the pump housing, the gears of the drive shaft and the 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 options are maintained even after prolonged periods of operation.
  • 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 invention has the particular advantage that the hard to reach area for cleaning between the drive shaft and the gear is kept free of paint residues.
  • the connecting means provided between the toothed wheel and the drive shaft can thus be made removable, without resulting in unwanted poorly flushable dead spaces.
  • the positive connections remain in a predefined manner. Gluing the connecting means between the drive shaft and the gear due to paint residues or other media can not occur.
  • the connection between the drive shaft and the gear can therefore be easily solved during maintenance.
  • the sealing means is preferably formed by two spaced sealing rings on the circumference of the drive shaft, wherein the distance between the sealing rings is equal to or smaller than the 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 the bore portions of the gear realize.
  • the sealing rings are held in the diameter steps between the drive shaft and the gear wheel, which enclose the diameter step for receiving the connecting means.
  • 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 shaping groove of the toothed wheel is preferably introduced into a bore shoulder of the toothed wheel formed between two diameters.
  • the pin secured in the drive shaft can thus be guided by simple insertion into the forming groove, so that the assembly of the gear and the drive shaft can be executed without much effort.
  • 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 stage of the drive shaft or the gear hole. This development of the invention is particularly suitable for applying the highest possible torques.
  • the connecting means with at least one faulty latch which is held on the circumference of the drive shaft and engages in a recess of the gear bore.
  • Both stepped and non-stepped drive shaft can be used here.
  • 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.
  • a seal housing is pressure-tight associated with the pump housing, which is penetrated by a concentric to the drive shaft recess of the drive shaft and which encloses a arranged on the circumference of the drive shaft sealant according to an advantageous embodiment of the invention.
  • the housing plate used for supporting the drive shaft can be made narrow in accordance with the storage requirements.
  • the sealants can get involved connect directly to the circumference of the drive shaft and are held by the seal housing sealingly on the housing plate.
  • a gland packing and a tensioning means is used, which acts on the packing gland.
  • This can be a seal against high operating pressures within the pump housing realize.
  • this also returns the respective color paint are possible to initiate, for example, a color change.
  • the drive shaft can be driven with changing direction of rotation.
  • a support bearing for radial and axial support of the drive shaft which is formed by a support ring or a rolling bearing.
  • the support ring or the rolling bearing are preferably held between a support housing and a shaft shoulder of the drive shaft.
  • the support housing is fixedly connected to the pump housing, wherein the seals for sealing the column caused by the drive shaft in the support housing or an upstream seal housing are arranged.
  • a shaft seal arranged on the circumference of the drive shaft and filled in the formed between the sealant and the shaft seal annulus at the periphery of the drive shaft, a barrier liquid.
  • a barrier liquid in this case, for example, a solvent-containing fluid is used.
  • the development of the invention is particularly advantageous, in which the annular space is connected via separate guide channels with an inlet and an outlet, wherein the inlet and the outlet are formed on the seal housing.
  • the fitting web is preferably arranged in the middle region of the gear wheel and executed with a fitting length of less than one quarter of the gear width. This makes it possible to realize a pendulum movement in the axial direction of the gear, which leads via the respective end faces associated sealing rings to an automatic centering of the gear and the drive shaft. However, manufacturing tolerances can be completely compensated for this and a wear-resistant and favorable start-up behavior of the gear end face relative to the housing plates can be realized.
  • Fig. 1 and Fig. 2 a first embodiment of the gear pump according to the invention is shown.
  • the Fig. 1 shows a view of the gear pump and in Fig. 2 a cross-sectional view of the gear pump is shown. Unless an explicit reference is made to one of the figures, 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 plates 1.1 and 1.2 middle plate 1.3 consists.
  • the housing plates 1.1 and 1.2 In the end faces of the housing plates 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 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 with a pump inlet 2 formed in the housing plate 2 and with a likewise in the housing plate 1.2 trained pump outlet 3 is connected.
  • 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 5 is rotatably mounted on a fixed bearing pin 21.
  • the bearing pin 21 is held for this purpose in a press bore 22 in the housing plate 1.1.
  • a sealing ring 1.6 is provided between the housing plate 1.1 and the bearing pin 21, a sealing ring 1.6 is provided.
  • 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 catch 10.
  • the catch 10 has at several points of the circumference of the drive shaft 7 a locking body 10.1, which is let into a shaft recess 11 and which is tensioned with a spring 10.2 acting radially outward.
  • operating position of 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 drive shaft 7 has a bearing end 7.1 and a coupling end 7.2.
  • the bearing end 7.1 of the drive shaft 7 is rotatably mounted within the pump housing.
  • the coupling end 7.2 of the drive shaft 7 protrudes outside of Pump housing 1 for coupling to a drive, not shown here.
  • the bearing end 7.1 of the drive shaft 7 is held with a free end in a bearing bag bore 16 on the housing plate 1.1 and forms a first bearing 8.1.
  • the drive shaft 7 is rotatably supported in the housing plate 1.2 in a continuous bearing bore 17 in a second bearing 8.2.
  • a shaft seal 20 is provided outside of the bearing 8.2 between the drive shaft 7 and the housing plate 1.2, so that the free coupling end 7.2 of the drive shaft 7 is pressure-tight out to a drive. Between the bearing 8.2 and the shaft seal 20, a diameter shoulder is formed in the drive shaft 7.
  • gaps are each formed directly or indirectly connected to the conveyor channel system 6 are.
  • gaps within the pump housing 1 allow a slight leakage of the subsidized paint, depending on the design of the gap seals, which penetrates in particular into the gaps between the gears 4 and 5 and the housing plates 1.1 and 1.2.
  • 7 sealant 14.1 and 14.2 are provided on the circumference of the drive shaft, which seal the gap between the gear 4 and the drive shaft 7.
  • 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 circumferentially 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 gear 4, so that the distance between the sealing rings 14.1 and 14.2 is substantially equal to the width of the gear 4.
  • an additional scavenging system is formed within the pump housing with a plurality of flushing channels in the housing plates 1.1 and 1.2 and in the drive shaft 7 and the bearing pin 21 to a supplied from the outside via a closable inlet 19 rinsing agent for rinsing the gaps between to flush the rotating and stationary components within the pump housing 1.
  • a scavenging system in a gear pump is for example from the EP 1 164 293 B1 known, so that at this point express reference to the description given there can be taken.
  • the inlet 19 opens into a recess of the bearing bag bore 16.
  • the rinsing agent is guided directly through 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.
  • 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 channel 18.4 is formed as a groove on the circumference of the drive shaft 7 and extends over the entire bearing point 8.2, so that the rinsing agent the bearing point 8.2 from the outside flows through inside.
  • the flushing channel 18.4 is formed as a groove on the circumference of the drive shaft 7 and extends over the entire bearing point 8.2, so that the rinsing agent the bearing point 8.2 from the outside flows through inside.
  • the detergent is performed in the conveyor channel system 6.
  • the outlet of the flushing agent via the pump inlet 2 and the pump outlet 3 can be realized.
  • 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. 1 and 2 illustrated embodiment of the gear pump according to the invention is particularly suitable to promote in Lackieranlagen color lakes, in which frequent color changes to change the color are required. Due to the design of the column and flushing channels all areas of the gear pumps are easily accessible before a color change to flush out paint residues.
  • Fig. 3 is a further embodiment of the gear pump according to the invention shown in a cross-sectional view.
  • the embodiment according to 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 gears 4 and 5 are held in a recess of the center plate 1.3.
  • the pump inlet 2 is in the housing plate 1.2 and the pump outlet 3 opposite in the housing plate 1.1 trained.
  • 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 drive shaft 7 penetrates the housing plate 1.2 in a bearing bore 17 and forms a bearing 8 of the drive shaft 7.
  • the seal housing 26 Within the seal housing 26 is concentric with the bearing bore 17 at the periphery of the drive shaft 7, a shaft seal in shape a gland packing 27 arranged.
  • the gland packing 27 is biased on one side by a clamping means 28 in the axial direction and pressed against the housing plate 1.2.
  • the clamping means 28 in the form of a spring is a clamping sleeve 29 on the circumference of the drive shaft 7 held and fixed relative to the sealing housing 26.
  • the coupling end 7.2 of the drive shaft 7 is shown cantilevered.
  • a shaft seal 39 is provided at the end of the clamping bush 28, a shaft seal 39 is provided.
  • 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 through the housing plates 1.1 and 1.2 and through the center plate 1.3 and driven by the gear 4 becomes.
  • 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 in Fig. 3 illustrated gear pump with a scavenging system run.
  • the gap formed in the bearing 8 between the drive shaft 7 and the housing plate 1.2 and the gaps formed between the end faces of the gears 4 and 5 and the housing plates 1.1 and 1.2 would be flushed through by a rinsing agent.
  • the scavenging system would be connected via a separate inlet and flushing channels with the conveyor channel system.
  • Fig. 4 and Fig. 5 is shown a further embodiment of the gear pump according to the invention.
  • the following description applies to both figures, insofar as no explicit reference is made to one of the figures.
  • Fig. 4 the gear pump is shown schematically in a cross-sectional view.
  • Fig. 5 shows a section of the cross-sectional view of the connection between the gear and the drive shaft.
  • the embodiment is in the structure 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 and 2 , so that reference is made to the above description at this point and only the differences will be explained.
  • the drive shaft 7 is rotatably supported via bearing bushes 31.1 and 31.2 in the bearing bag bore 16 of the housing plate 1.1 and in the bearing bore 17 of the housing plate 1.2.
  • the driven gear 4 is connected to one another at the bearing end 7.1 of the drive shaft 7 via a connecting means 9.
  • the housing plate 1.1, the center plate 1.3 and the housing plate 1.2 are pressure-tightly connected to each other, wherein on the housing plate 1.2 a pump inlet 2 and the housing plate 1.1 a pump outlet (not shown here) are formed, which are interconnected within the pump housing 1 via a conveyor channel system 6 are.
  • the follower gear 5 is mounted on the bearing bush 31.3 on the circumference of the journal 21.
  • the bearing pin 21 is held in the press bore 22 of the housing plate 1.1.
  • the connecting means 9 between the drive shaft 7 and the gear 4 is formed by a polygonal shape 30.
  • the bore 12 of the gear 4 and the circumference of the drive shaft 7 is stepped in several diameter steps.
  • a first extending from the bearing end 7.1 diameter stage 23.1 is designed as a sealing surface, wherein a circumferential sealing groove 15.1 on the circumference of the drive shaft 7 cooperates with a corresponding sealing surface on the bore 12 of the gear 4.
  • a polygonal shape 30 is formed on the circumference of the drive shaft 7 and in the bore 12.
  • the polygonal shape 30 is in Fig. 5 shown schematically.
  • the polygonal shape 30 is exemplified by a hexagon.
  • a second sealing surface between the gear 4 and the drive shaft 7 is formed in a diameter larger diameter stage 23.3.
  • the sealing groove 15.2 is formed on the circumference of the drive shaft 7, in which the sealing ring 14.2 is held.
  • the sealing ring 14.2 is supported on an opposite sealing surface of the bore 12.
  • 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 a diameter shoulder 40 in the end region, against which a support ring 34 rests.
  • the support ring 34 is L-shaped and is held in a recess of a support housing 33.
  • the support housing 33 is penetrated by the drive shaft 7 and projects with the free coupling end 7.2 for connecting a drive from the support housing 33 out.
  • a shaft seal 39 is disposed within the support housing 33 on the circumference of the drive shaft.
  • the support housing 33 is pressure-tightly connected via a seal housing 26 to the pump housing 1.
  • a first housing seal 32.1 is arranged concentrically with the bearing bore 10 and between the seal housing 26 and the support housing 34, a second housing seal 32.2.
  • the seal housing 26 has a recess formed concentrically to the drive shaft 7, which serves for receiving a stuffing box 27 arranged on the circumference of the drive shaft 7.
  • the gland packing 27 is supported on the pump housing 1 facing the end of the Seal housing 26 directly on the housing plate 1.2 from.
  • a clamping means 28 is provided in the seal housing 26.
  • 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.
  • This in Fig. 4 and 5 illustrated embodiment of the gear pump according to the invention is particularly suitable to carry out the metering of paint colors with high operating pressures.
  • a return of the gear pump is set in a color change to initiate a color change.
  • the forces acting from the outside on the drive shaft 7 can be absorbed by the support bearing of the support ring in the support housing 33, so that the gears in the interior of the pump housing 1 are free of axial forces. This is particularly the signs of wear on the driven gear 4 reduce.
  • the support ring 34 can thus also be replaced by a conventional rolling bearing.
  • the scavenging system 18 formed within the pump housing is identical to the embodiment according to FIG Fig. 1 and 2 executed, so that at this point no further explanation is done.
  • 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.
  • Fig. 6 is a further embodiment of a gear pump according to the invention shown schematically in a cross-sectional view.
  • the exemplary embodiment is essentially identical to the exemplary embodiment according to FIG Fig. 3 , so that only the differences will be explained below and otherwise reference is made to the above description.
  • the drive shaft 7 is mounted within the formed by the housing plates 1.1, 1.2 and 1.3 pump housing 1 in the bearings 8.1 and 8.2.
  • the bearing 8.1 is formed in the housing plate 1.1, which has a storage bag bore 16 for this purpose.
  • the second bearing 8.2 is formed by the bearing bore 17 of the housing plate 1.2.
  • 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 between the diameter portion of the diameter stage 23.2 and the bore 12 of the gear 4 is also formed, so that the gear around the fitting web 42 can perform 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 sealing rings 14.1 and 14.2 are arranged for this purpose on the circumference of the drive shaft in the respective sections of the diameter stages 23.1 and 23.2. This allows complete tolerances such as the parallelism of the housing plates 1.1 and 1.2 with respect to the gear end faces of the gear 4 completely compensate.
  • the gear 4 can be particularly wear-resistant between the housing plates 1.1 and 1.2.
  • 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.
  • 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.
  • Fig. 6 illustrated embodiment is thus particularly suitable to absorb external forces acting on the drive shaft 7 forces by the rolling 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.
  • the fitting web 42 is preferably arranged in the central region of the gear 4 and executed with a fitting length which is smaller than one quarter of the gear width.
  • the fitting web 42 can alternatively be formed on the circumference of the bore 12 of the gear 4. In the remaining areas between the drive shaft 7 and the gear 4 Passungsdream are provided in order to obtain sufficient mobility of the gear 4.
  • FIGS. 1 to 6 illustrated embodiments of the gear pump according to the invention are exemplary in their structure and design of the individual components.
  • the selected between the drive shaft 7 and the gear 4 examples of the connecting means 9 can be replaced by other constructive solutions.
  • Essential here, however, is; in that the one or more gaps forming between the toothed wheel and the drive shaft are respectively sealed off towards the front sides of the toothed wheel, so that no leakage occurs from the outside can get between the drive shaft and the gear.

Landscapes

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

Claims (18)

  1. Pompe à engrenages avec deux roues dentées (4, 5) s'engrenant entraînées par un arbre d'entraînement (7) et avec un tenon de palier de roulement (21) disposé de façon à pouvoir tourner à l'intérieur d'un carter de pompe (1) et formant un système de canal d'extraction (6) entre une admission de pompe (2) et une sortie de pompe (3) et avec plusieurs fentes formées entre le carter de pompe (1), les roues dentées (4, 5), l'arbre d'entraînement (7) et le tenon de palier de roulement (21), une des fentes étant formée entre l'arbre d'entraînement (7) et une des roues dentées (4) et un moyen de liaison (9) étant disposé dans la fente pour réaliser la liaison solidaire en rotation de l'arbre d'entraînement (7) avec la roue dentée (4), caractérisée en ce que la fente est étanchéifiée en direction des côtés avant de la roue dentée (4), entre l'arbre d'entraînement (7) et la roue dentée (4), par le biais d'un moyen d'étanchéité (14.1, 14.2).
  2. Pompe à engrenages selon la revendication 1, caractérisée en ce que les moyens d'étanchéité sont formés par au moins deux bagues d'étanchéité (14.1, 14.2) placées à une certaine distance l'une de l'autre au niveau de la périphérie de l'arbre d'entraînement (7), la distance entre les bagues d'étanchéité (14.1, 14.2) étant inférieure ou égale à la largeur de la roue dentée (4).
  3. Pompe à engrenages selon la revendication 2, caractérisée en ce que les bagues d'étanchéité (14.1, 14.2) sont maintenues dans les rainures d'étanchéité (15.1, 15.2) tournant dans le plan radial dans la périphérie de l'arbre d'entraînement (7) et/ou dans les rainures d'étanchéité (15.1, 15.2) tournant dans le plan radial dans la périphérie d'un alésage (12) de la roue dentée (4).
  4. Pompe à engrenages selon l'une quelconque des revendications 1 à 3, caractérisée en ce que plusieurs pas diamétraux (23.1, 23.2) sont formés entre l'arbre d'entraînement (7) et la roue dentée (4), le moyen de liaison (9) étant maintenu entre l'arbre d'entraînement (7) et la roue dentée (4) dans un des pas diamétraux (23.2).
  5. Pompe à engrenages selon la revendication 4, caractérisée en ce que les bagues d'étanchéité (14.1, 14.2) sont maintenues dans les pas diamétraux (23.1, 23.2) entre l'arbre d'entraînement (7) et la roue dentée (4), lesdits pas diamétraux incluant le pas diamétral (23.2) servant à la réception du moyen de liaison (9).
  6. Pompe à engrenages selon la revendication 4 ou 5, caractérisée en ce que le moyen de liaison (9) est formé par une tige (24) reliée fixement à l'arbre d'entraînement (7) et s'engrenant dans une rainure moulée (25) de la roue dentée (4).
  7. Pompe à engrenages selon la revendication 6, caractérisée en ce que la rainure moulée (25) de la roue dentée (4) est amenée dans le plan axial dans un talon d'alésage formé entre deux pas diamétraux (23.2, 23.3).
  8. Pompe à engrenages selon la revendication 4 ou 5, caractérisée en ce que le moyen de liaison (9) prend une forme de polygone (30) de l'arbre d'entraînement (7) entrant en interaction avec une forme de polygone (30) de l'alésage (12) de la roue dentée (4).
  9. Pompe à engrenages selon l'une quelconque des revendications 1 à 5, caractérisée en ce que le moyen de liaison (9) est formé par au moins un cran (10) sollicité par ressort maintenu au niveau de la périphérie de l'arbre d'entraînement (7) et s'engrenant dans un évidement (13) de l'alésage de roue dentée (12).
  10. Pompe à engrenages selon l'une quelconque des revendications 1 à 9, caractérisée en ce qu'un système de canal de lavage (18) est prévu pour laver les fentes à l'intérieur du carter de pompe (1) à travers lequel une amenée (19) séparée est reliée au système de canal d'extraction.
  11. Pompe à engrenages selon la revendication 10, caractérisée en ce que le système de canal de lavage (18) comporte plusieurs canaux de lavage (18.1, 18.8) à travers lesquels plusieurs points de palier de roulement (8.1, 8.2) de l'arbre d'entraînement (7) peuvent être nettoyés sur toute leur longueur, respectivement de l'extérieur vers l'intérieur.
  12. Pompe à engrenages selon l'une quelconque des revendications 1 à 11, caractérisée en ce que le carter de pompe (1) est réalisé en plusieurs parties, les côtés avant des roues dentées (4, 5) étant maintenus entre deux plaques de carter (1.1, 1.2) et l'arbre d'entraînement (7) étant maintenu de façon à pouvoir tourner dans les points de palier de roulement (8.1, 8.2) avec respectivement une section d'arbre directement placée dans les alésages de réception (16, 17) des plaques de carter.
  13. Pompe à engrenages selon l'une quelconque des revendications 1 à 12, caractérisée en ce qu'un carter d'étanchéité (26) est disposé de façon étanche à la pression au niveau du carter de pompe (1), ledit carter étant traversé par l'arbre d'entraînement (7) dans un évidement réalisé concentriquement par rapport à l'arbre d'entraînement (7) et enceignant un moyen d'étanchéité (27) disposé au niveau de la périphérie de l'arbre d'entraînement (7).
  14. Pompe à engrenages selon l'une quelconque des revendications 1 à 13, caractérisée en ce qu'un support d'appui (34, 33, 26, 41) est réalisé au niveau d'une section de couplage, saillant à l'extérieur du carter de pompe (1), de l'arbre d'entraînement (7) pour le soutien radial et axial de l'arbre d'entraînement (7) formé par une bague de maintien (34) ou un palier de roulement à rouleau (41).
  15. Pompe à engrenages selon la revendication 14, caractérisée en ce qu'une bague d'étanchéité d'arbre (39) est disposée à l'intérieur d'un carter de maintien (33), au niveau de la périphérie de l'arbre d'entraînement (7), et que l'espace annulaire (35) réalisé entre le moyen d'étanchéité (27) et la bague d'étanchéité d'arbre (39) est rempli avec un liquide de blocage au niveau de la périphérie de l'arbre d'entraînement (7).
  16. Pompe à engrenages selon la revendication 15, caractérisée en ce que l'espace annulaire (35) est relié à une admission (37) et une sortie (38) via des canaux (36.1, 36.2) séparés et que l'admission (37) et la sortie (38) sont réalisées au niveau du carter d'étanchéité (26).
  17. Pompe à engrenages selon l'une quelconque des revendications 1 à 16, caractérisée en ce qu'un étai d'ajustement (42) tournant est réalisé au niveau de la périphérie de l'alésage (12) de la roue dentée (4) ou au niveau de la périphérie de l'arbre d'entraînement (7) à travers lequel la roue dentée (4) est maintenue librement sans jeu au niveau de l'arbre d'entraînement (7).
  18. Pompe à engrenages selon la revendication 17, caractérisée en ce que l'étai d'ajustement (42) est disposé dans la région centrale de la roue dentée (4) et comporte une longueur d'ajustement inférieure à un quart de la largeur de roue dentée.
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 EP2122175A1 (fr) 2009-11-25
EP2122175B1 true 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
EP3089639B1 (fr) 2014-01-03 2018-07-11 Koninklijke Douwe Egberts B.V. Bloc d'alimentation échangeable pour machine de distribution de boisson, doseur, ensemble pompe et procédé de fabrication
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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US259640A (en) * 1882-06-13 Joseph h
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US2801593A (en) * 1954-05-03 1957-08-06 Roper Corp Geo D Rotary pump
US2997960A (en) * 1957-12-20 1961-08-29 Kimijima Takehiko Gear pump
US3059584A (en) * 1960-01-13 1962-10-23 Sonic Eng Corp Rotary pumps and compressors
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EP0497995A1 (fr) * 1991-02-01 1992-08-12 Leybold Aktiengesellschaft Pompe sèche à vide
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Also Published As

Publication number Publication date
CN101657643B (zh) 2012-12-26
ZA200905633B (en) 2010-05-26
KR20100015624A (ko) 2010-02-12
PT2122175E (pt) 2015-11-12
EP2122175A1 (fr) 2009-11-25
KR101503088B1 (ko) 2015-03-16
WO2008113712A1 (fr) 2008-09-25
RU2435073C2 (ru) 2011-11-27
ES2550459T3 (es) 2015-11-10
HUE025876T2 (en) 2016-04-28
PL2122175T3 (pl) 2016-04-29
US9004890B2 (en) 2015-04-14
CN101657643A (zh) 2010-02-24
US20100278676A1 (en) 2010-11-04
RU2009138374A (ru) 2011-04-27
MX2009010073A (es) 2010-01-20

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