EP2550456B1 - Gear pump - Google Patents

Gear pump Download PDF

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Publication number
EP2550456B1
EP2550456B1 EP20110709925 EP11709925A EP2550456B1 EP 2550456 B1 EP2550456 B1 EP 2550456B1 EP 20110709925 EP20110709925 EP 20110709925 EP 11709925 A EP11709925 A EP 11709925A EP 2550456 B1 EP2550456 B1 EP 2550456B1
Authority
EP
European Patent Office
Prior art keywords
shaft
pump
housing
brake
pump 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
EP20110709925
Other languages
German (de)
French (fr)
Other versions
EP2550456A2 (en
Inventor
Ulrich Helbing
Arkardiusz Tomzik
Dietrich Witzler
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Oerlikon Textile GmbH and Co KG
Original Assignee
Oerlikon Textile GmbH and Co KG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Oerlikon Textile GmbH and Co KG filed Critical Oerlikon Textile GmbH and Co KG
Publication of EP2550456A2 publication Critical patent/EP2550456A2/en
Application granted granted Critical
Publication of EP2550456B1 publication Critical patent/EP2550456B1/en
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
    • 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
    • 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
    • F04C11/00—Combinations of two or more machines or pumps, each being of rotary-piston or oscillating-piston type; Pumping installations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0003—Sealing arrangements in rotary-piston machines or pumps
    • F04C15/0023—Axial sealings for working fluid
    • F04C15/0026—Elements specially adapted for sealing of the lateral faces of intermeshing-engagement type machines or pumps, e.g. gear machines or pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
    • F04C15/0084—Brakes, braking assemblies
    • 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
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C18/14—Rotary-piston pumps specially adapted for elastic fluids 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
    • F04C18/16—Rotary-piston pumps specially adapted for elastic fluids 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 helical teeth, e.g. chevron-shaped, screw type
    • 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
    • F04C2/02—Rotary-piston machines or pumps of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • 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
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • 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
    • F04C2210/00—Fluid
    • F04C2210/20—Fluid liquid, i.e. incompressible
    • 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
    • F04C2240/30—Casings or housings
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S415/00—Rotary kinetic fluid motors or pumps
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S417/00—Pumps

Definitions

  • the invention relates to a gear pump according to the preamble of claim 1.
  • gear pumps are used in which the medium to be conveyed is transported by the teeth of two intermeshing gears between a pump inlet and a pump outlet.
  • gear pumps are preferably used to generate uniform flow rates such as the provision of paints in a paint shop.
  • Such a gear pump is for example from the DE 10 2005 059 563 A1 known.
  • two intermeshing gears are rotatably supported within a pump housing and connected to a pump shaft.
  • the pump shaft protrudes with a coupling end of the pump housing and can be coupled with a drive shaft of a motor.
  • the gears held in the pump housing are driven by the torque transmitted to the pump shaft.
  • a brake ring is arranged, which acts with at least one braking surface on a friction surface of the pump shaft or on a friction surface of the pump housing.
  • the invention is characterized in that a load reversal at the gears is intercepted by acting on the pump shaft braking torque and does not continue in the entire drive train. As a result, only the games between the tooth flanks of the gears, which affect the conveying uniformity but only slightly.
  • Another advantage of the invention is that independent of the selected seals within the pump defined and relatively high braking torques can be generated on the pump shaft. In addition, no higher friction torques can be generated via sealing lips of the usual seals, since they wear out in the shortest possible time and lead to failure.
  • the brake ring offers the advantage of tuning both the braking surface and the material of the brake ring to the generation of the braking torque. Depending on the location of the Brake ring can be formed on the pump shaft or on the pump housing, the corresponding friction surface.
  • the formation of the gear pump according to the invention according to the embodiment in which the brake ring is rotatably held in the pump housing and in which the braking surface is formed on an inner diameter of the brake ring.
  • the friction surface of the pump shaft is preferably formed on the circumference as a circumferential surface whose outer diameter has an excess against the inner diameter of the brake ring. This can already set a predefined bias between the brake ring and the pump shaft.
  • the brake ring has a plurality of evenly distributed on the inner diameter arranged brake segments, each forming a partial braking surface.
  • the development of the invention is preferably carried out in which the brake segments are formed on a support ring to a component in which the brake segments laterally axially outstanding the carrier are arranged and in which the brake segments are held by a comprehensive spring ring on the circumference of the pump shaft.
  • each of the brake segments is pressed uniformly over the spring ring on the circumference of the pump shaft, so that the partial braking surfaces of the brake segments interact with the circumferential friction surface of the pump shaft.
  • the pump housing has a plurality of housing plates and a shaft housing, wherein the pump shaft is mounted in the outer housing plates and protrudes with the coupling end in the shaft housing and wherein the brake ring is disposed on a shaft portion of the pump shaft within the shaft housing. So it is possible to arrange the brake ring outside the housing plates.
  • a shaft seal is provided which is assigned to the shaft portion of the pump shaft between a bearing and the brake ring.
  • the sealing surface formed on the circumference of the pump shaft can thus be formed and machined independently of the revolving friction surface. This way, each shaft section can be sealed to the relevant function or optimally adjusted to decelerate.
  • the development of the gear pump according to the invention is particularly advantageous, in which a support bearing for radial and axial support of the pump shaft is formed within the shaft housing.
  • the support bearing is assigned to the shaft section of the pump shaft between the brake ring and the coupling end.
  • the brake ring at a distance from the braking surface has a circumferential sealing lip for sealing, on the circumference of the pump shaft is applied.
  • the two functions braking the pump shaft and sealing the pump shaft can be combined with each other and run through a brake ring.
  • the gear pump consists of a pump housing 1.
  • the pump housing 1 is constructed in several parts and has a plurality of housing plates 1.1, 1.2 and 1.3 and a shaft housing 1.4.
  • Within a central housing plate 1.3 is a recess for two intermeshing gears 3 and 4 included.
  • the middle housing plate 1.3 is held with the gears 3 and 4 between the outer housing plates 1.1 and 1.2.
  • In the end faces of the outer housing plates 1.1 and 1.2 each have a sealing ring 1.5 and 1.6 are arranged, through which the gaps between the middle housing plate 1.3 and the outer housing plates 1.1 and 1.2 are sealed to the outside.
  • One of the gears 3 is fixedly connected to a rotatable bearing shaft 6.
  • the bearing shaft 6 is held in two bushings 6.1 and 6.2, which are embedded in the outer housing plates 1.1 and 1.2.
  • the second gear 4 is rotatably held on a pump shaft 5.
  • the pump shaft 5 is rotatably mounted with a plurality of shaft sections in the housing plates 1.1 and 1.2.
  • the housing plate 1.1 has a first bearing bore 7.1 and the second housing plate 1.2 has a second bearing bore 7.2, in which the bearing bushes 8.1 and 8.2 are held.
  • the bearing bore 7.1 is formed as a blind hole in the housing plate 1.1.
  • the bearing bore 7.2 in the housing plate 1.2 is continuous, so that the pump shaft 5 protrudes from the outer housing plate 1.2.
  • the outside of the outer housing plate 1.2 projecting shaft portion of the pump shaft 5 forms a coupling end 5.1, on which a profiling 5.2 is formed.
  • a pump inlet 2 and a pump outlet not shown here is arranged, which form a conveyor channel system for the metered delivery of a flowable medium with the gears 3 and 4.
  • the outside of the housing plate 1.2 outstanding shaft portion of the pump shaft 5 is surrounded by the shaft housing 1.4.
  • the shaft housing 1.4 is for this purpose firmly connected to the housing plate 1.2.
  • a receiving bore 10 is formed, in which a coupling sleeve 9 is rotatably guided.
  • the coupling sleeve 9 is connected at one end face on the profiling 5.2 with the pump shaft 5.
  • the coupling sleeve 9 has a profile opening to be coupled to a drive shaft of a drive.
  • the coupling sleeve 9 is held by a locking ring 12 in the shaft housing 1.4, which has a receiving opening 13 in the axial extension of the coupling sleeve 9.
  • the pump can be coupled via a plug connection with a drive.
  • the shaft housing 1.4 On the side of the housing plate 1.2, the shaft housing 1.4 has a concentric with the pump shaft 5 arranged recess 31, in which a brake ring 11 is held against rotation.
  • the brake ring 11 has at its inner diameter to a braking surface 11.1, which corresponds to a formed on the pump shaft 5 friction surface 5.3.
  • the friction surface 5.3 is formed as a circumferential lateral surface on the circumference of the pump shaft 5.
  • the inner diameter of the brake ring 11 relative to the outer diameter of the pump shaft 5 in the shaft portion of the friction surface 5.3 a defined undersize, so that the brake ring 11 exerts a contact pressure on the pump shaft 5.
  • a braking torque is thereby generated via the brake ring 11.
  • the nature of the friction surface 5.3 on the pump shaft 5 and the nature of the braking surface 11.1 on the brake ring 11 and beyond the material of the brake ring 11 can be adapted to each other.
  • the brake ring 11 is formed of a wear-resistant plastic.
  • a shaft sealing ring 14 is provided within the housing plate 1.2 in the region between the bearing bush 8.2 and the brake ring 11, which is assigned to the shaft portion of the pump shaft 5 between the bearing point and the friction surface 5.3.
  • the shaft seal 14 is between the housing plates 1.1, 1.2 and 1.3 formed conveyor channel system sealed to the outside in the area of the pump shaft 5.
  • the pump shaft 5 is driven via the coupling sleeve 9 by a coupled drive at a predetermined speed during operation.
  • the gears 3 and 4 engage each other and convey a supplied via the pump inlet 2 medium continuously to a pump outlet.
  • an outlet pressure prevailing at the pump outlet is higher than an inlet pressure at the inlet side of the pump, a continuous flow through the gears 3 and 4 results for each revolution of the pump shaft 5.
  • additional hydraulic forces act on the gears 3 and 4, which act in the conveying direction.
  • Fig. 2 is a further embodiment of a gear pump according to the invention shown, which substantially with the embodiment according to Fig. 1 is identical, so that only the differences will be explained below and otherwise referred to the above description.
  • the pump shaft 5 has a cylindrical coupling end 5.1, which protrudes from the shaft housing 1.4 and, for example, via a feather key with a drive can be coupled.
  • a brake ring 11 is assigned in a shaft portion between the coupling end 5.1 and a shaft seal 14 of the pump shaft 5.
  • the brake ring 11 is held against rotation in a recess 31 of the shaft housing 1.4.
  • Fig. 3 shows a sectional view of the brake ring 11 on the circumference of the pump shaft 5.
  • FIGS. 2 and 3 the following description applies to both FIGS. 2 and 3 ,
  • the brake ring 11 is formed in this embodiment by a support ring 15 and a plurality of laterally arranged on the support ring 15 brake segments 16.
  • the carrier ring 15 and the brake segments 16 are combined to form a component, wherein the brake segments 16 are elastically connected to the carrier ring 15.
  • the brake segments 16 protrude axially relative to the carrier ring 15 and are uniformly distributed over the circumference of the carrier ring 15.
  • the individual brake segments 16 have on an inner side in each case a partial braking surface 16.1, which rest on the circumference of the pump shaft 5 and cooperate with the friction surface of the pump shaft 5 5.3.
  • a spring ring 17 is provided, which spans the brake segments 16 and holds with a predefined bias on the circumference of the pump shaft 5.
  • the circumferentially distributed brake segments 16 are formed identically and have in the radial direction at an equal distance from each other. Both the symmetrical arrangement of the brake segments and the distances between the brake segments can be distributed differently over the circumference.
  • Fig. 4 is shown a further embodiment of a gear pump according to the invention, as it is preferably used for metering paints in paint shops.
  • Fig. 4 is the pump housing 1 also formed in several parts.
  • the gear 3 is rotatably held in this embodiment on a bearing pin 18 which is held in a pin bore 19 of the outer housing plate 1.1.
  • a sealing ring 20 is arranged in the housing plate 1.1, through which the pin bore 19 is sealed to the outside.
  • the second gear 4 is held by a connecting means 21 directly on the circumference of the pump shaft 5.
  • the axial gap formed between the circumference of the pump shaft 5 and the gear 4 becomes both Pages of the gear 4 sealed by the O-rings 22.1 and 22.2.
  • the pump shaft 5 is mounted directly in the outer housing plates 1.1 and 1.2. In this case, no bushings are provided and the pump shaft 5 is guided directly into the bearing bores 7.1 and 7.2.
  • a plurality of flushing channels 23 are formed in the pump shaft 5, the housing plates 1.1 and 1.2 and the bearing pin 18 to completely rinse the interior of the pump housing 1 for the purpose of a delivery medium change.
  • a purge system for a gear pump is for example from the EP 1 164 293 A2 known, so that at this point reference can be made to the description given there and no further explanation is given here.
  • a shaft seal 14, a brake ring 11, and a support bearing 24 are formed between the coupling end 5.1 and the bearing.
  • the shaft seal 14, the brake ring 11 and the support bearing 24 are held by the shaft housing 1.4 concentric with the pump shaft 5.
  • the shaft housing 1.4 is for this purpose firmly connected to the housing plate 1.2.
  • the brake ring 11 is also formed by a support ring 15 and a plurality of laterally molded brake segments 16.
  • Fig. 5 is a cross-sectional view of the brake ring 11 is shown.
  • the support ring 15 at an inner diameter on a circumferential sealing lip 25.
  • the sealing lip 25 is formed at a distance from the partial braking surfaces 16.1 of the brake segments 16 on the brake ring 11, so that the brake ring 11 performs a double function on the circumference of the pump shaft 5 in this case.
  • the integrally formed on the support ring 15 brake segments 16 are pressed by a spring ring 17 to the friction surface 5.3 of the pump shaft 5 to generate a braking torque.
  • the support ring 15 with its peripheral to the inner diameter sealing lip 25 on the circumference of the pump shaft 5 adjacent to the friction surface 5.3 and forms a seal in the shaft housing 1.4 relative to the coupling end 5.1.
  • a closed annular space 26 is formed within the shaft housing 1.4 by the shaft seal 14 and the brake ring 11.
  • open channels 27 through which a barrier liquid can be introduced into the annulus.
  • the channels 27 in the shaft housing 1.4 are closable, so that in the operating state a barrier fluid can be held within the annular space 26.
  • a barrier liquid a solvent-containing fluid is preferably used as a function of the pumped medium in order to dissolve the leaked through gap leakage media, in this case paints within the annular space 29, so that hardening and sticking in the gaps are prevented.
  • the trained between the coupling end 5.1 and the brake ring 11 support bearing 24 is formed in this embodiment by a rolling bearing that is disposed between a shaft shoulder 28 of the pump shaft 5 and a housing shoulder 29 of the shaft housing 1.4.
  • About the shaft shoulder 28 and the housing shoulder 29 can advantageously record axially acting forces on the pump shaft 5.
  • the forces acting from the outside over the coupling end 5.1 of the pump shaft 5 forces are intercepted by the support bearing 24 and not directed into the interior of the pump housing 1.
  • the coupling end 5.1 of the pump shaft 5 is identical to the embodiment according to Fig. 1
  • the coupling sleeve 9 is held in the receiving bore 10 of the shaft housing 1.4 by a bearing sleeve 30, which simultaneously represents a bearing point for a detachable drive shaft.
  • In the drive shaft can be introduced via the receiving opening 13 at the end of the shaft housing 1.4 and connect via the coupling sleeve 9 with the pump shaft 5.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Valves And Accessory Devices For Braking Systems (AREA)

Description

Die Erfindung betrifft eine Zahnradpumpe gemäß dem Oberbegriff des Anspruchs 1.The invention relates to a gear pump according to the preamble of claim 1.

Es ist allgemein bekannt, dass zum Fördern und Dosieren von Fluiden Zahnradpumpen verwendet werden, bei welchen das zu fördernde Medium durch die Verzahnung zweier ineinander greifende Zahnräder zwischen einem Pumpeneinlass und einem Pumpenauslass transportiert wird. Durch die Mehrzahl der Förderglieder lassen sich somit sehr gleichmäßige Fördervolumen einstellen, so dass derartige Zahnradpumpen bevorzugt zum Erzeugen gleichmäßiger Fördermengen wie beispielsweise das Bereitstellen von Lacken in einer Lackieranlage verwendet werden.It is well known that for pumping and metering of fluids, gear pumps are used in which the medium to be conveyed is transported by the teeth of two intermeshing gears between a pump inlet and a pump outlet. By the majority of the conveyor members can thus be adjusted very uniform flow rates, so that such gear pumps are preferably used to generate uniform flow rates such as the provision of paints in a paint shop.

Eine derartige Zahnradpumpe ist beispielsweise aus der DE 10 2005 059 563 A1 bekannt. Bei der bekannten Zahnradpumpe sind zwei ineinander greifende Zahnräder innerhalb eines Pumpengehäuses drehbar gehalten und mit einer Pumpenwelle verbunden. Die Pumpenwelle ragt mit einem Kupplungsende aus dem Pumpengehäuse heraus und lässt sich mit einer Antriebswelle eines Motors kuppeln. Beim Einsatz derartiger Zahnradpumpen mit wechselnden Druckbelastungen auf der Auslassseite oder der Einlassseite oder beiden Seiten wurden Ungleichmäßigkeiten des Förderstromes beobachtet. Üblicherweise werden die in dem Pumpengehäuse gehaltenen Zahnräder durch das auf die Pumpenwelle übertragene Drehmoment angetrieben. Für den Fall, dass durch Druckschwankungen eine Umkehr der Druckdifferenzen zwischen dem Pumpeneinlass und dem Pumpenauslass eintritt, wirken neben dem Drehmoment der Pumpenwelle zusätzliche Druckkräfte auf die Zahnflanken der Zahnräder in Förderrichtung ein, so dass je nach Größe der Druckkräfte an den Zahnrädern eine Umkehr von einem motorischen Antrieb zu einem eigenständigen Antrieb erfolgen kann. Dieser Wechsel in der Lastrichtung pflanzt sich über den gesamten Antriebsstrang fort. Aufgrund der Verdrehspiele in dem Antriebsstrang kommt es nun zum Beschleunigen und wieder Abbremsen der Drehgeschwindigkeit der Zahnräder innerhalb einer Umdrehung der Pumpenwelle. Diese Erscheinung führt unmittelbar zu einer Ungleichmäßigkeit im Förderstrom während einer Umdrehung der Pumpenwelle. Eine weitere bekannte Zahnradpumpe gemäß dem Oberbegriff des Anspruchs 1 wird in der Patentschrift WO2008/113712 beschrieben. Es ist daher Aufgabe der Erfindung, eine Zahnradpumpe der gattungsgemäßen Art derart weiterzubilden, dass unabhängig von den Druckverhältnissen am Pumpeneingang und Pumpenausgang ein möglichst gleichmäßiger Förderstrom erzeugbar ist.Such a gear pump is for example from the DE 10 2005 059 563 A1 known. In the known gear pump, two intermeshing gears are rotatably supported within a pump housing and connected to a pump shaft. The pump shaft protrudes with a coupling end of the pump housing and can be coupled with a drive shaft of a motor. When using such gear pumps with changing pressure loads on the outlet side or the inlet side or both sides unevenness of the flow rate were observed. Usually, the gears held in the pump housing are driven by the torque transmitted to the pump shaft. In the event that a reversal of the pressure differences between the pump inlet and the pump outlet occurs due to pressure fluctuations, act in addition to the torque of the pump shaft additional pressure forces on the tooth flanks of the gears in the conveying direction, so that, depending on the size of the pressure forces on the gears, a reversal of a motor drive can be made to a standalone drive. This change in the load direction is planted on the entire powertrain away. Due to the torsional backlash in the drive train, it now comes to accelerate and slow down the rotational speed of the gears within a revolution of the pump shaft. This phenomenon immediately leads to unevenness in the flow rate during one revolution of the pump shaft. Another known gear pump according to the preamble of claim 1 is in the patent WO2008 / 113712 described. It is therefore an object of the invention to develop a gear pump of the generic type such that regardless of the pressure conditions at the pump inlet and pump outlet as uniform as possible flow is generated.

Diese Aufgabe wird erfindungsgemäß dadurch gelöst, dass am Umfang der Pumpenwelle ein Bremsring angeordnet ist, der mit zumindest einer Bremsfläche auf eine Reibfläche der Pumpenwelle oder auf eine Reibfläche des Pumpengehäuses wirkt.This object is achieved in that at the periphery of the pump shaft, a brake ring is arranged, which acts with at least one braking surface on a friction surface of the pump shaft or on a friction surface of the pump housing.

Vorteilhafte Weiterbildungen der Erfindung sind durch die Merkmale und Merkmalskombinationen der jeweiligen Unteransprüche definiert.Advantageous developments of the invention are defined by the features and feature combinations of the respective subclaims.

Die Erfindung zeichnet sich dadurch aus, dass eine Lastumkehr an den Zahnrädern durch ein an der Pumpenwelle wirkendes Bremsmoment abgefangen wird und sich nicht in den gesamten Antriebsstrang fortsetzt. Dadurch wirken nur die Spiele zwischen den Zahnflanken der Zahnräder, die die Fördergleichmäßigkeit jedoch nur unwesentlich beeinflussen. Ein weiterer Vorteil der Erfindung liegt darin, dass unabhängig von den gewählten Dichtungen innerhalb der Pumpe definierte und relativ hohe Bremsmomente an der Pumpenwelle erzeugt werden können. Zudem können über Dichtlippen der üblichen Dichtungen keine höheren Reibmomente erzeugt werden, da diese in kürzester Zeit verschleißen und zu einem Ausfall führen. Insoweit bietet der Bremsring den Vorteil, sowohl die Bremsfläche als auch das Material des Bremsringes auf die Erzeugung des Bremsmomentes hin abzustimmen. Je nach Anbringungsort des Bremsringes kann dabei die korrespondierende Reibfläche an der Pumpenwelle oder an dem Pumpengehäuse ausgebildet sein.The invention is characterized in that a load reversal at the gears is intercepted by acting on the pump shaft braking torque and does not continue in the entire drive train. As a result, only the games between the tooth flanks of the gears, which affect the conveying uniformity but only slightly. Another advantage of the invention is that independent of the selected seals within the pump defined and relatively high braking torques can be generated on the pump shaft. In addition, no higher friction torques can be generated via sealing lips of the usual seals, since they wear out in the shortest possible time and lead to failure. In that regard, the brake ring offers the advantage of tuning both the braking surface and the material of the brake ring to the generation of the braking torque. Depending on the location of the Brake ring can be formed on the pump shaft or on the pump housing, the corresponding friction surface.

Besonders bevorzugt ist jedoch die Ausbildung der erfindungsgemäßen Zahnradpumpe gemäß der Weiterbildung, bei welcher der Bremsring drehsicher in dem Pumpengehäuse gehalten ist und bei welcher die Bremsfläche an einem Innendurchmesser des Bremsrings ausgebildet ist.However, particularly preferred is the formation of the gear pump according to the invention according to the embodiment, in which the brake ring is rotatably held in the pump housing and in which the braking surface is formed on an inner diameter of the brake ring.

In diesem Fall wird die Reibfläche der Pumpenwelle bevorzugt am Umfang als umlaufende Mantelfläche ausgebildet, deren Außendurchmesser gegen den Innendurchmesser des Bremsringes ein Übermaß aufweist. Damit lässt sich bereits eine vordefinierte Vorspannung zwischen dem Bremsring und der Pumpenwelle einstellen.In this case, the friction surface of the pump shaft is preferably formed on the circumference as a circumferential surface whose outer diameter has an excess against the inner diameter of the brake ring. This can already set a predefined bias between the brake ring and the pump shaft.

Alternativ besteht jedoch auch die Möglichkeit, dass der Bremsring mehrere am Innendurchmesser gleichmäßig verteilt angeordnete Bremssegmente aufweist, die jeweils eine Teilbremsfläche bilden. Damit können vorteilhaft Stick-Slip-Effekte zwischen dem Bremsring und der Pumpenwelle vermieden werden.Alternatively, however, it is also possible that the brake ring has a plurality of evenly distributed on the inner diameter arranged brake segments, each forming a partial braking surface. Thus, advantageous stick-slip effects between the brake ring and the pump shaft can be avoided.

Um einerseits eine einfache Montage zu ermöglichen und andererseits eine definierte Vorspannung zwischen dem Bremsring und der Pumpenwelle zu erhalten, ist die Weiterbildung der Erfindung bevorzugt ausgeführt, bei welcher die Bremssegmente an einem Trägerring zu einem Bauteil geformt sind, bei welchem die Bremssegmente seitlich axial hervorragend an dem Träger angeordnet sind und bei welchem die Bremssegmente durch einen umfassenden Federring am Umfang der Pumpenwelle gehalten sind. Damit wird jeder der Bremssegmente gleichmäßig über den Federring am Umfang der Pumpenwelle gedrückt, so dass die Teilbremsflächen der Bremssegmente mit der umlaufenden Reibfläche der Pumpenwelle zusammenwirken.On the one hand to allow easy mounting and on the other hand to obtain a defined bias between the brake ring and the pump shaft, the development of the invention is preferably carried out in which the brake segments are formed on a support ring to a component in which the brake segments laterally axially outstanding the carrier are arranged and in which the brake segments are held by a comprehensive spring ring on the circumference of the pump shaft. Thus, each of the brake segments is pressed uniformly over the spring ring on the circumference of the pump shaft, so that the partial braking surfaces of the brake segments interact with the circumferential friction surface of the pump shaft.

Für eine nachträgliche Integration eines derartigen Bremsringes in einer Zahnradpumpe ist die Weiterbildung der Erfindung besonders geeignet, bei welcher das Pumpengehäuse mehrere Gehäuseplatten und ein Wellengehäuse aufweist, wobei die Pumpenwelle in den äußeren Gehäuseplatten gelagert ist und mit dem Kupplungsende in das Wellengehäuse ragt und wobei der Bremsring an einem Wellenabschnitt der Pumpenwelle innerhalb des Wellengehäuses angeordnet ist. So besteht die Möglichkeit, den Bremsring außerhalb der Gehäuseplatten anzuordnen.For a subsequent integration of such a brake ring in a gear pump, the development of the invention is particularly suitable wherein the pump housing has a plurality of housing plates and a shaft housing, wherein the pump shaft is mounted in the outer housing plates and protrudes with the coupling end in the shaft housing and wherein the brake ring is disposed on a shaft portion of the pump shaft within the shaft housing. So it is possible to arrange the brake ring outside the housing plates.

Für höhere Betriebsdrücke ist insbesondere die Weiterbildung der Zahnradpumpe geeignet, bei welcher innerhalb einer der Gehäuseplatten und/oder des Wellengehäuses an der Pumpenwelle ein Wellendichtring vorgesehen ist, der dem Wellenabschnitt der Pumpenwelle zwischen einer Lagerstelle und dem Bremsring zugeordnet ist. So sind die Funktionen zwischen der Abdichtung der Pumpenwelle und dem Abbremsen der Pumpenwelle klar voneinander getrennt. Die am Umfang der Pumpenwelle ausgebildete Dichtfläche lässt sich somit unabhängig von der umlaufenden Reibfläche ausbilden und bearbeiten. So lässt sich jeder Wellenabschnitt auf die betreffende Funktion abdichten oder Abbremsen optimal einstellen.For higher operating pressures in particular the development of the gear pump is suitable, in which within one of the housing plates and / or the shaft housing on the pump shaft, a shaft seal is provided which is assigned to the shaft portion of the pump shaft between a bearing and the brake ring. Thus, the functions between the sealing of the pump shaft and the deceleration of the pump shaft are clearly separated. The sealing surface formed on the circumference of the pump shaft can thus be formed and machined independently of the revolving friction surface. This way, each shaft section can be sealed to the relevant function or optimally adjusted to decelerate.

Um möglichst die im Innern des Pumpengehäuses auf die Pumpenwelle wirkenden inneren Druckkräfte gegenüber dem Bremsring abzufangen, ist die Weiterbildung der Erfindungsgemäßen Zahnradpumpe besonders vorteilhaft, bei welcher innerhalb des Wellengehäuses eine Stützlagerung zur radialen und axialen Abstützung der Pumpenwelle ausgebildet ist. Das Stützlager ist hierzu dem Wellenabschnitt der Pumpenwelle zwischen dem Bremsring und dem Kupplungsende zugeordnet.In order to intercept as far as possible the internal pressure forces acting on the pump shaft in the interior of the pump housing relative to the brake ring, the development of the gear pump according to the invention is particularly advantageous, in which a support bearing for radial and axial support of the pump shaft is formed within the shaft housing. For this purpose, the support bearing is assigned to the shaft section of the pump shaft between the brake ring and the coupling end.

Grundsätzlich ist es auch möglich, den Bremsring auf einer Außenseite der Stützlagerung anzuordnen.In principle, it is also possible to arrange the brake ring on an outer side of the support bearing.

Um die Funktionalität des Bremsringes bei geeigneten Werkstoffen noch weiter zu erhöhen, ist gemäß einer vorteilhaften Weiterbildung vorgesehen, dass der Bremsring im Abstand zu der Bremsfläche eine umlaufende Dichtlippe zur Abdichtung aufweist, die am Umfang der Pumpenwelle anliegt. Damit lassen sich die beiden Funktionen Abbremsen der Pumpenwelle und Abdichten der Pumpenwelle miteinander kombinieren und durch einen Bremsring ausführen.In order to increase the functionality of the brake ring with suitable materials even further, is provided according to an advantageous development that the brake ring at a distance from the braking surface has a circumferential sealing lip for sealing, on the circumference of the pump shaft is applied. Thus, the two functions braking the pump shaft and sealing the pump shaft can be combined with each other and run through a brake ring.

Damit lassen sich vorteilhaft hohe Dichtheiten gegenüber dem Kupplungsende der Pumpenwelle realisieren, wobei der Bremsring und der Wellendichtring zwischen sich einen Ringraum am Umfang der Pumpenwelle bilden, der mit einer Sperrflüssigkeit befüllbar ist, so dass eine zusätzliche Barriere gebildet ist. Zudem lassen sich durch entsprechende Wahl der Sperrflüssigkeit Ablagerungen und Alterungsvorgänge des Fördermediums vermeiden. So sind derartige Zahnradpumpen besonders zum Fördern und Dosieren von Farblacken geeignet.This can be realized advantageously high tightness against the coupling end of the pump shaft, wherein the brake ring and the shaft seal between them form an annular space on the circumference of the pump shaft, which can be filled with a barrier liquid, so that an additional barrier is formed. In addition, deposits and aging processes of the pumped medium can be avoided by appropriate choice of barrier fluid. Thus, such gear pumps are particularly suitable for conveying and dosing of colored lacquers.

Die erfindungsgemäße Zahnradpumpe wird nachfolgend anhand einiger Ausführungsbeispiele unter Hinweis auf die beigefügten Figuren näher erläutert.The gear pump according to the invention will be explained in more detail with reference to some embodiments with reference to the accompanying figures.

Es stellen dar:

Fig. 1
schematisch eine Querschnittansicht eines ersten Ausführungsbeispiels der erfindungsgemäßen Zahnradpumpe
Fig. 2
schematisch eine Querschnittansicht eines weiteren Ausführungsbeispiels der erfindungsgemäßen Zahnradpumpe
Fig. 3
schematisch eine Schnittdarstellung eines am Umfang der Pumpenwelle gehaltenen Bremsringes
Fig. 4
schematisch eine Querschnittansicht eines weiteren Ausführungsbeispiels der erfindungsgemäßen Zahnradpumpe
Fig. 5
schematisch eine Querschnittansicht des an der Pumpenwelle gehaltenen Bremsringes des Ausführungsbeispiels nach Fig. 4
They show:
Fig. 1
schematically a cross-sectional view of a first embodiment of the gear pump according to the invention
Fig. 2
schematically a cross-sectional view of another embodiment of the gear pump according to the invention
Fig. 3
schematically a sectional view of a held on the circumference of the pump shaft brake ring
Fig. 4
schematically a cross-sectional view of another embodiment of the gear pump according to the invention
Fig. 5
schematically a cross-sectional view of the held on the pump shaft brake ring of the embodiment according to Fig. 4

In Fig. 1 ist ein erstes Ausführungsbeispiel der erfindungsgemäßen Zahnradpumpe dargestellt. Die Zahnradpumpe besteht aus einem Pumpengehäuse 1. Das Pumpengehäuse 1 ist mehrteilig aufgebaut und weist mehrere Gehäuseplatten 1.1, 1.2 und 1.3 sowie ein Wellengehäuse 1.4 auf. Innerhalb einer mittelern Gehäuseplatte 1.3 ist eine Aussparung für zwei ineinandergreifende Zahnräder 3 und 4 enthalten. Die mittlere Gehäuseplatte 1.3 wird mit den Zahnrädern 3 und 4 zwischen den äußeren Gehäuseplatten 1.1 und 1.2 gehalten. In den Stirnseiten der äußeren Gehäuseplatten 1.1 und 1.2 ist jeweils ein Dichtring 1.5 und 1.6 angeordnet, durch welche die Spalte zwischen der mittleren Gehäuseplatte 1.3 und den äußeren Gehäuseplatten 1.1 und 1.2 nach außen hin abgedichtet sind.In Fig. 1 a first embodiment of the gear pump according to the invention is shown. The gear pump consists of a pump housing 1. The pump housing 1 is constructed in several parts and has a plurality of housing plates 1.1, 1.2 and 1.3 and a shaft housing 1.4. Within a central housing plate 1.3 is a recess for two intermeshing gears 3 and 4 included. The middle housing plate 1.3 is held with the gears 3 and 4 between the outer housing plates 1.1 and 1.2. In the end faces of the outer housing plates 1.1 and 1.2 each have a sealing ring 1.5 and 1.6 are arranged, through which the gaps between the middle housing plate 1.3 and the outer housing plates 1.1 and 1.2 are sealed to the outside.

Eines der Zahnräder 3 ist fest mit einer drehbaren Lagerwelle 6 verbunden. Die Lagerwelle 6 ist in zwei Lagerbuchsen 6.1 und 6.2 gehalten, die in den äußeren Gehäuseplatten 1.1 und 1.2 eingelassen sind. Das zweite Zahnrad 4 ist auf einer Pumpenwelle 5 drehfest gehalten. Die Pumpenwelle 5 ist mit mehreren Wellenabschnitten in den Gehäuseplatten 1.1 und 1.2 drehbar gelagert. Hierzu weist die Gehäuseplatte 1.1 eine erste Lagerbohrung 7.1 und die zweite Gehäuseplatte 1.2 eine zweite Lagerbohrung 7.2 auf, in welchen die Lagerbuchsen 8.1 und 8.2 gehalten sind. Die Lagerbohrung 7.1 ist als eine Sacklochbohrung in der Gehäuseplatte 1.1 ausgebildet. Demgegenüber ist die Lagerbohrung 7.2 in der Gehäuseplatte 1.2 durchgehend, so dass die Pumpenwelle 5 aus der äußeren Gehäuseplatte 1.2 hervorragt. Der außerhalb der äußeren Gehäuseplatte 1.2 ragende Wellenabschnitt der Pumpenwelle 5 bildet ein Kupplungsende 5.1, an welchem eine Profilierung 5.2 ausgebildet ist.One of the gears 3 is fixedly connected to a rotatable bearing shaft 6. The bearing shaft 6 is held in two bushings 6.1 and 6.2, which are embedded in the outer housing plates 1.1 and 1.2. The second gear 4 is rotatably held on a pump shaft 5. The pump shaft 5 is rotatably mounted with a plurality of shaft sections in the housing plates 1.1 and 1.2. For this purpose, the housing plate 1.1 has a first bearing bore 7.1 and the second housing plate 1.2 has a second bearing bore 7.2, in which the bearing bushes 8.1 and 8.2 are held. The bearing bore 7.1 is formed as a blind hole in the housing plate 1.1. In contrast, the bearing bore 7.2 in the housing plate 1.2 is continuous, so that the pump shaft 5 protrudes from the outer housing plate 1.2. The outside of the outer housing plate 1.2 projecting shaft portion of the pump shaft 5 forms a coupling end 5.1, on which a profiling 5.2 is formed.

In der Gehäuseplatte 1.2 ist ein Pumpeneinlass 2 sowie ein hier nicht dargestellter Pumpenauslass angeordnet, die mit den Zahnrädern 3 und 4 ein Förderkanalsystem zur dosierten Förderung eines fließfähigen Mediums bilden.In the housing plate 1.2, a pump inlet 2 and a pump outlet not shown here is arranged, which form a conveyor channel system for the metered delivery of a flowable medium with the gears 3 and 4.

Der außerhalb der Gehäuseplatte 1.2 herausragende Wellenabschnitt der Pumpenwelle 5 ist von dem Wellengehäuse 1.4 umgeben. Das Wellengehäuse 1.4 ist hierzu fest mit der Gehäuseplatte 1.2 verbunden. Innerhalb des Wellengehäuses 1.4 ist eine Aufnahmebohrung 10 ausgebildet, in welcher eine Kupplungshülse 9 drehbar geführt ist. Die Kupplungshülse 9 ist an einer Stirnseite über die Profilierung 5.2 mit der Pumpenwelle 5 verbunden. Auf der gegenüberliegenden Seite weist die Kupplungshülse 9 eine Profilöffnung auf, um mit einer Antriebswelle eines Antriebes gekoppelt zu werden. Die Kupplungshülse 9 ist über einen Sicherungsring 12 im Wellengehäuse 1.4 gehalten, das in axialer Verlängerung zur Kupplungshülse 9 eine Aufnahmeöffnung 13 aufweist. Somit lässt sich die Pumpe über eine Steckverbindung mit einem Antrieb koppeln.The outside of the housing plate 1.2 outstanding shaft portion of the pump shaft 5 is surrounded by the shaft housing 1.4. The shaft housing 1.4 is for this purpose firmly connected to the housing plate 1.2. Within the shaft housing 1.4 a receiving bore 10 is formed, in which a coupling sleeve 9 is rotatably guided. The coupling sleeve 9 is connected at one end face on the profiling 5.2 with the pump shaft 5. On the opposite side, the coupling sleeve 9 has a profile opening to be coupled to a drive shaft of a drive. The coupling sleeve 9 is held by a locking ring 12 in the shaft housing 1.4, which has a receiving opening 13 in the axial extension of the coupling sleeve 9. Thus, the pump can be coupled via a plug connection with a drive.

An der Seite der Gehäuseplatte 1.2 weist das Wellengehäuse 1.4 eine konzentrisch zu der Pumpenwelle 5 angeordnete Aussparung 31 auf, in welcher ein Bremsring 11 drehsicher gehalten ist. Der Bremsring 11 weist an seinem Innendurchmesser eine Bremsfläche 11.1 auf, die mit einer an der Pumpenwelle 5 ausgebildeten Reibfläche 5.3 korrespondiert. Die Reibfläche 5.3 ist als umlaufende Mantelfläche am Umfang der Pumpenwelle 5 ausgebildet. Im entlasteten Zustand weist der Innendurchmesser des Bremsringes 11 gegenüber dem Außendurchmesser der Pumpenwelle 5 im Wellenabschnitt der Reibfläche 5.3 ein definiertes Untermaß auf, so dass der Bremsring 11 ein Anpressdruck auf die Pumpenwelle 5 ausübt. Bei Drehung der Pumpenwelle 5 wird über den Bremsring 11 dadurch ein Bremsmoment erzeugt.On the side of the housing plate 1.2, the shaft housing 1.4 has a concentric with the pump shaft 5 arranged recess 31, in which a brake ring 11 is held against rotation. The brake ring 11 has at its inner diameter to a braking surface 11.1, which corresponds to a formed on the pump shaft 5 friction surface 5.3. The friction surface 5.3 is formed as a circumferential lateral surface on the circumference of the pump shaft 5. In the unloaded state, the inner diameter of the brake ring 11 relative to the outer diameter of the pump shaft 5 in the shaft portion of the friction surface 5.3 a defined undersize, so that the brake ring 11 exerts a contact pressure on the pump shaft 5. Upon rotation of the pump shaft 5, a braking torque is thereby generated via the brake ring 11.

Um eine definierte Größe des Bremsmomentes zu erhalten, können die Beschaffenheit der Reibfläche 5.3 an der Pumpenwelle 5 sowie die Beschaffenheit der Bremsfläche 11.1 am Bremsring 11 und darüber hinaus der Werkstoff des Bremsringes 11 aufeinander angepasst werden. Üblicherweise wird der Bremsring 11 aus einem verschleißfesten Kunststoff gebildet.In order to obtain a defined magnitude of the braking torque, the nature of the friction surface 5.3 on the pump shaft 5 and the nature of the braking surface 11.1 on the brake ring 11 and beyond the material of the brake ring 11 can be adapted to each other. Usually, the brake ring 11 is formed of a wear-resistant plastic.

Zur Abdichtung des Pumpengehäuses 1 ist innerhalb der Gehäuseplatte 1.2 im Bereich zwischen der Lagerbuchse 8.2 und dem Bremsring 11 ein Wellendichtring 14 vorgesehen, der dem Wellenabschnitt der Pumpenwelle 5 zwischen der Lagerstelle und der Reibfläche 5.3 zugeordnet ist. Durch den Wellendichtring 14 wird der zwischen den Gehäuseplatten 1.1, 1.2 und 1.3 gebildetes Förderkanalsystem nach außen hin im Bereich der Pumpenwelle 5 abgedichtet.For sealing the pump housing 1, a shaft sealing ring 14 is provided within the housing plate 1.2 in the region between the bearing bush 8.2 and the brake ring 11, which is assigned to the shaft portion of the pump shaft 5 between the bearing point and the friction surface 5.3. By the shaft seal 14 is between the housing plates 1.1, 1.2 and 1.3 formed conveyor channel system sealed to the outside in the area of the pump shaft 5.

Bei dem in Fig. 1 dargestellten Ausführungsbeispiel der erfindungsgemäßen Zahnradpumpe wird im Betrieb die Pumpenwelle 5 über die Kupplungshülse 9 durch einen angekoppelten Antrieb mit vorbestimmter Drehzahl angetrieben. In diesem Zustand greifen die Zahnräder 3 und 4 ineinander und fördern ein über den Pumpeneinlass 2 zugeführten Mediums kontinuierlich zu einem Pumpenauslass. Für den Fall, dass ein am Pumpenauslass vorherrschender Auslassdruck höher ist als ein Einlassdruck auf der Einlassseite der Pumpe ergibt sich bei jeder Umdrehung der Pumpenwelle 5 ein kontinuierlicher durch die Zahnräder 3 und 4 bestimmter Förderstrom. Für den Fall, dass aufgrund von Druckschwankungen eine Umkehr der zwischen dem Pumpeneinlass und dem Pumpenauslass wirkenden Druckdifferenz eintritt, wirken zusätzliche hydraulische Kräfte auf die Zahnräder 3 und 4 ein, die in Förderrichtung wirken. Dabei können Zustände auftreten, dass eine Voreilung gegenüber dem Fremdantrieb erfolgt, die sich im Rahmen der konstruktiv bedingten Passungsspiele auswirkt. Um derartige Betriebszustände in engen Grenzen zu halten, wird über den Bremsring 11 kontinuierlich an der Pumpenwelle 5 ein Bremsmoment erzeugt. Das Bremsmoment ist derart ausgelegt, dass ein Voreilen der Pumpenwelle gegenüber einer Antriebswelle verhindert wird. Somit lassen sich ungewünschte Lastwechsel vorteilhaft unterdrücken, so dass keine Förderstromschwankungen während einer Umdrehung der Pumpe eintreten können. Durch die Abbremsung der Pumpenwelle 5 werden vorteilhaft gleichmäßige Förderströme auch bei schwankenden Druckverhältnissen zwischen Pumpeneinlass und Pumpenauslass erreicht.At the in Fig. 1 illustrated embodiment of the gear pump according to the invention, the pump shaft 5 is driven via the coupling sleeve 9 by a coupled drive at a predetermined speed during operation. In this state, the gears 3 and 4 engage each other and convey a supplied via the pump inlet 2 medium continuously to a pump outlet. In the event that an outlet pressure prevailing at the pump outlet is higher than an inlet pressure at the inlet side of the pump, a continuous flow through the gears 3 and 4 results for each revolution of the pump shaft 5. In the event that a reversal of the pressure difference acting between the pump inlet and the pump outlet occurs due to pressure fluctuations, additional hydraulic forces act on the gears 3 and 4, which act in the conveying direction. In this case, conditions may occur that a lead over the third party drive takes place, which has an effect in the context of the design-related Passungsspiele. In order to keep such operating conditions within narrow limits, a braking torque is generated continuously on the pump shaft 5 via the brake ring 11. The braking torque is designed such that a lead of the pump shaft relative to a drive shaft is prevented. Thus, unwanted load changes can be advantageously suppressed, so that no flow fluctuations during one revolution of the pump can occur. Due to the deceleration of the pump shaft 5 advantageously uniform flow rates are achieved even with fluctuating pressure conditions between the pump inlet and pump outlet.

Je nach Ausführung der Pumpe können unterschiedliche Ausführungsformen zur zusätzlichen Abbremsung der Pumpenwelle genutzt werden. So wäre bei dem Ausführungsbeispiel nach Fig. 1 ebenfalls möglich, dass der Bremsring 11 drehsicher mit der Pumpenwelle 5 verbunden ist und mit einer äußeren Bremsfläche auf eine in dem Wellengehäuse 1.4 ausgebildeten Reibfläche zusammenwirkt. Die Reibfläche an dem Wellengehäuse könnte dabei durch eine Bohrung oder Flanken einer Nut gebildet sein. In Praxis hat sich jedoch die alternative Variante der Erfindung besonders bewährt, bei welcher der Bremsring drehsicher in einem Gehäuseteil gehalten ist.Depending on the design of the pump, different embodiments can be used for additional braking of the pump shaft. So would be in the embodiment after Fig. 1 also possible that the brake ring 11 is rotatably connected to the pump shaft 5 and formed with an outer braking surface on one in the shaft housing 1.4 Friction surface cooperates. The friction surface on the shaft housing could be formed by a bore or flanks of a groove. In practice, however, the alternative variant of the invention has proven particularly useful, in which the brake ring is held against rotation in a housing part.

In Fig. 2 ist ein weiteres Ausführungsbeispiel einer erfindungsgemäßen Zahnradpumpe gezeigt, das im Wesentlichen mit dem Ausführungsbeispiel nach Fig. 1 identisch ist, so dass nachfolgend nur die Unterschiede erläutert werden und ansonsten zu der vorgenannten Beschreibung Bezug genommen wird.In Fig. 2 is a further embodiment of a gear pump according to the invention shown, which substantially with the embodiment according to Fig. 1 is identical, so that only the differences will be explained below and otherwise referred to the above description.

Bei dem Ausführungsbeispiel nach Fig. 2 weist die Pumpenwelle 5 ein zylindrisches Kupplungsende 5.1 auf, welches aus dem Wellengehäuse 1.4 herausragt und beispielsweise über eine Passfeder mit einem Antrieb kuppelbar ist.According to the embodiment Fig. 2 the pump shaft 5 has a cylindrical coupling end 5.1, which protrudes from the shaft housing 1.4 and, for example, via a feather key with a drive can be coupled.

In einem Wellenabschnitt zwischen dem Kupplungsende 5.1 und einem Wellendichtring 14 ist der Pumpenwelle 5 ein Bremsring 11 zugeordnet. Der Bremsring 11 ist in einer Aussparung 31 des Wellengehäuses 1.4 drehsicher gehalten.In a shaft portion between the coupling end 5.1 and a shaft seal 14 of the pump shaft 5, a brake ring 11 is assigned. The brake ring 11 is held against rotation in a recess 31 of the shaft housing 1.4.

Zur weiteren Erläuterung des Bremsringes 11 wird neben der Fig. 2 zusätzlich Bezug zu der Fig. 3 genommen. Die Fig. 3 zeigt eine Schnittdarstellung des Bremsringes 11 am Umfang der Pumpenwelle 5. Insoweit gilt die nachfolgende Beschreibung für beide Figuren 2 und 3.For further explanation of the brake ring 11 is in addition to the Fig. 2 additionally related to the Fig. 3 taken. The Fig. 3 shows a sectional view of the brake ring 11 on the circumference of the pump shaft 5. In this respect, the following description applies to both FIGS. 2 and 3 ,

Der Bremsring 11 wird in diesem Ausführungsbeispiel durch einen Trägerring 15 und eine Mehrzahl seitlich an dem Trägerring 15 angeordnete Bremssegmente 16 gebildet. Der Trägerring 15 und die Bremssegmente 16 sind zu einem Bauteil vereint, wobei die Bremssegmente 16 elastisch mit dem Trägerring 15 verbunden sind. Die Bremssegmente 16 ragen axial gegenüber dem Trägerring 15 hervor und sind gleichmäßig über den Umfang des Trägerrings 15 verteilt ausgebildet. Die einzelnen Bremssegmente 16 weisen an einer Innenseite jeweils eine Teilbremsfläche 16.1 auf, die am Umfang der Pumpenwelle 5 anliegen und mit der Reibfläche 5.3 der Pumpenwelle 5 zusammenwirken. Um alle Bremssegmente 16 gemeinsam am Umfang der Pumpenwelle 5 zu führen, ist ein Federring 17 vorgesehen, der die Bremssegmente 16 umspannt und mit einer vordefinierten Vorspannung am Umfang der Pumpenwelle 5 hält. Durch die Anzahl der an dem Trägerring 15 gehaltenen Bremssegmente 16 sowie durch die radiale Ausdehnung der Bremssegmente 16 sind zusätzliche Parameter gegeben, um bestimmte Bremseigenschaften an der Pumpenwelle 5 zu erzeugen. Bei dem dargestellten Ausführungsbeispiel sind die am Umfang verteilten Bremssegmente 16 identisch ausgebildet und weisen in radialer Richtung einen gleichgroßen Abstand zueinander auf. Sowohl die symmetrische Anordnung der Bremssegmente als auch die Abstände zwischen den Bremssegmenten können über den Umfang verteilt unterschiedlich ausgebildet sein.The brake ring 11 is formed in this embodiment by a support ring 15 and a plurality of laterally arranged on the support ring 15 brake segments 16. The carrier ring 15 and the brake segments 16 are combined to form a component, wherein the brake segments 16 are elastically connected to the carrier ring 15. The brake segments 16 protrude axially relative to the carrier ring 15 and are uniformly distributed over the circumference of the carrier ring 15. The individual brake segments 16 have on an inner side in each case a partial braking surface 16.1, which rest on the circumference of the pump shaft 5 and cooperate with the friction surface of the pump shaft 5 5.3. In order to guide all brake segments 16 together on the circumference of the pump shaft 5, a spring ring 17 is provided, which spans the brake segments 16 and holds with a predefined bias on the circumference of the pump shaft 5. By the number of held on the support ring 15 brake segments 16 and by the radial extent of the brake segments 16 additional parameters are given to produce certain braking properties on the pump shaft 5. In the illustrated embodiment, the circumferentially distributed brake segments 16 are formed identically and have in the radial direction at an equal distance from each other. Both the symmetrical arrangement of the brake segments and the distances between the brake segments can be distributed differently over the circumference.

Die Funktion des in Fig. 2 dargestellten Ausführungsbeispiels ist identisch zu dem Ausführungsbeispiel nach Fig. 1, so dass an dieser Stelle keine weiteren Erläuterungen erfolgen.The function of in Fig. 2 illustrated embodiment is identical to the embodiment according to Fig. 1 , so that at this point no further explanation.

In Fig. 4 ist ein weiteres Ausführungsbeispiel einer erfindungsgemäßen Zahnradpumpe gezeigt, wie sie vorzugsweise zur Dosierung von Lacken in Lackieranlagen eingesetzt wird.In Fig. 4 is shown a further embodiment of a gear pump according to the invention, as it is preferably used for metering paints in paint shops.

Bei dem Ausführungsbeispiel nach Fig. 4 ist das Pumpengehäuse 1 ebenfalls mehrteilig ausgebildet. Das Zahnrad 3 ist in diesem Ausführungsbeispiel drehbar an einem Lagerzapfen 18 gehalten, der in einer Zapfenbohrung 19 der äußeren Gehäuseplatte 1.1 gehalten ist. Konzentrisch zu den Lagerzapfen 18 ist in der Gehäuseplatte 1.1 ein Dichtring 20 angeordnet, durch welche die Zapfenbohrung 19 nach außen hin abgedichtet ist.According to the embodiment Fig. 4 is the pump housing 1 also formed in several parts. The gear 3 is rotatably held in this embodiment on a bearing pin 18 which is held in a pin bore 19 of the outer housing plate 1.1. Concentric with the bearing pin 18, a sealing ring 20 is arranged in the housing plate 1.1, through which the pin bore 19 is sealed to the outside.

Das zweite Zahnrad 4 ist durch ein Verbindungsmittel 21 direkt am Umfang der Pumpenwelle 5 gehalten. Der sich zwischen dem Umfang der Pumpenwelle 5 und dem Zahnrad 4 ausbildende axiale Spalt wird zu beiden Seiten des Zahnrades 4 durch die O-Ringe 22.1 und 22.2 gedichtet. Damit wird einerseits ein Eindringen des Fördermediums in den Spalt zwischen dem Zahnrad 4 und der Pumpenwelle 5 vermieden und andererseits eine in Abhängigkeit von dem verwendeten Verbindungsmittel 21 gewisse Beweglichkeit des Zahnrades 4 an der Pumpenwelle 5 erreicht. Damit können insbesondere die durch stirnseitigen Anlauf zwischen dem Zahnrad 4 und den Gehäuseplatten 1.1 und 1.2 verursachten Verschleißerscheinungen vorteilhaft vergleichmäßigt bzw. vermindert werden.The second gear 4 is held by a connecting means 21 directly on the circumference of the pump shaft 5. The axial gap formed between the circumference of the pump shaft 5 and the gear 4 becomes both Pages of the gear 4 sealed by the O-rings 22.1 and 22.2. Thus, on the one hand penetration of the pumped medium into the gap between the gear 4 and the pump shaft 5 is avoided and on the other hand reaches a certain function of the connecting means 21 certain mobility of the gear 4 on the pump shaft 5. Thus, in particular caused by frontal start between the gear 4 and the housing plates 1.1 and 1.2 signs of wear can be advantageously evened out or reduced.

Die Pumpenwelle 5 ist unmittelbar in den äußeren Gehäuseplatten 1.1 und 1.2 gelagert. In diesem Fall sind keine Lagerbuchsen vorgesehen und die Pumpenwelle 5 ist direkt in den Lagerbohrungen 7.1 und 7.2 geführt.The pump shaft 5 is mounted directly in the outer housing plates 1.1 and 1.2. In this case, no bushings are provided and the pump shaft 5 is guided directly into the bearing bores 7.1 and 7.2.

Darüber hinaus sind in der Pumpenwelle 5, den Gehäuseplatten 1.1 und 1.2 sowie dem Lagerzapfen 18 mehrere Spülkanäle 23 ausgebildet, um den Innenraum des Pumpengehäuses 1 zum Zwecke eines Fördermediumwechsels vollständig ausspülen zu können. Ein derartiges Spülsystem für eine Zahnradpumpe ist beispielsweise aus der EP 1 164 293 A2 bekannt, so dass an dieser Stelle Bezug zu der dort angegebenen Beschreibung genommen werden kann und hier keine weiteren Erläuterungen dazu abgegeben werden.In addition, a plurality of flushing channels 23 are formed in the pump shaft 5, the housing plates 1.1 and 1.2 and the bearing pin 18 to completely rinse the interior of the pump housing 1 for the purpose of a delivery medium change. Such a purge system for a gear pump is for example from the EP 1 164 293 A2 known, so that at this point reference can be made to the description given there and no further explanation is given here.

An dem außerhalb der äußeren Gehäuseplatte 1.2 herausragenden Wellenabschnitt der Pumpenwelle 5 sind zwischen dem Kupplungsende 5.1 und der Lagerstelle ein Wellendichtring 14, ein Bremsring 11, und ein Stützlager 24 ausgebildet. Der Wellendichtring 14, der Bremsring 11 und die Stützlagerung 24 sind durch das Wellengehäuse 1.4 konzentrisch zur Pumpenwelle 5 gehalten. Das Wellengehäuse 1.4 ist hierzu fest mit der Gehäuseplatte 1.2 verbunden. Bei dem in Fig. 4 dargestellten Ausführungsbeispiel ist der Bremsring 11 ebenfalls durch einen Trägerring 15 und mehrere seitlich angeformte Bremssegmente 16 gebildet.At the outside of the outer housing plate 1.2 outstanding shaft portion of the pump shaft 5, a shaft seal 14, a brake ring 11, and a support bearing 24 are formed between the coupling end 5.1 and the bearing. The shaft seal 14, the brake ring 11 and the support bearing 24 are held by the shaft housing 1.4 concentric with the pump shaft 5. The shaft housing 1.4 is for this purpose firmly connected to the housing plate 1.2. At the in Fig. 4 illustrated embodiment, the brake ring 11 is also formed by a support ring 15 and a plurality of laterally molded brake segments 16.

Zur Erläuterung des in diesem Ausführungsbeispiel eingesetzten Bremsringes 11 wird zusätzlich zu der Fig. 4 auch zu Fig. 5 Bezug genommen. In Fig. 5 ist eine Querschnittansicht des Bremsringes 11 gezeigt. Wie aus der Fig. 5 hervorgeht, weist der Trägerring 15 an einem Innendurchmesser eine umlaufende Dichtlippe 25 auf. Die Dichtlippe 25 ist mit Abstand zu den Teilbremsflächen 16.1 der Bremssegmente 16 an dem Bremsring 11 ausgebildet, so dass der Bremsring 11 in diesem Fall eine Doppelfunktion am Umfang der Pumpenwelle 5 ausführt. Einerseits werden die an dem Trägerring 15 angeformten Bremssegmente 16 über einen Federring 17 an die Reibfläche 5.3 der Pumpenwelle 5 gedrückt um ein Bremsmoment zu erzeugen. Gleichzeitig wird der Trägerring 15 mit seiner am Innendurchmesser umlaufenden Dichtlippe 25 am Umfang der Pumpenwelle 5 neben der Reibfläche 5.3 und bildet eine Abdichtung in dem Wellengehäuse 1.4 gegenüber dem Kupplungsende 5.1.To explain the brake ring 11 used in this embodiment is in addition to the Fig. 4 also to Fig. 5 Referenced. In Fig. 5 is a cross-sectional view of the brake ring 11 is shown. Like from the Fig. 5 shows, the support ring 15 at an inner diameter on a circumferential sealing lip 25. The sealing lip 25 is formed at a distance from the partial braking surfaces 16.1 of the brake segments 16 on the brake ring 11, so that the brake ring 11 performs a double function on the circumference of the pump shaft 5 in this case. On the one hand, the integrally formed on the support ring 15 brake segments 16 are pressed by a spring ring 17 to the friction surface 5.3 of the pump shaft 5 to generate a braking torque. At the same time, the support ring 15 with its peripheral to the inner diameter sealing lip 25 on the circumference of the pump shaft 5 adjacent to the friction surface 5.3 and forms a seal in the shaft housing 1.4 relative to the coupling end 5.1.

Bei dem in Fig. 4 dargestellten Ausführungsbeispiel wird durch den Wellendichtring 14 und dem Bremsring 11 ein geschlossener Ringraum 26 innerhalb des Wellengehäuses 1.4 gebildet. In dem Ringraum 26 münden Kanäle 27, durch welche eine Sperrflüssigkeit in den Ringraum eingeleitet werden kann. Die Kanäle 27 in dem Wellengehäuse 1.4 sind verschließbar, so dass im Betriebszustand eine Sperrflüssigkeit innerhalb des Ringraumes 26 gehalten werden kann. Als Sperrflüssigkeit wird in Abhängigkeit von dem Fördermedium vorzugsweise ein lösemittelhaltiges Fluid eingesetzt, um die durch Spaltleckagen ausgetretenen Fördermedien, in diesem Fall Lacke, innerhalb des Ringraumes 29 zu lösen, so dass Verhärtungen und Verklebungen in den Spalten verhindert werden.At the in Fig. 4 illustrated embodiment, a closed annular space 26 is formed within the shaft housing 1.4 by the shaft seal 14 and the brake ring 11. In the annular space 26 open channels 27 through which a barrier liquid can be introduced into the annulus. The channels 27 in the shaft housing 1.4 are closable, so that in the operating state a barrier fluid can be held within the annular space 26. As a barrier liquid, a solvent-containing fluid is preferably used as a function of the pumped medium in order to dissolve the leaked through gap leakage media, in this case paints within the annular space 29, so that hardening and sticking in the gaps are prevented.

Die zwischen dem Kupplungsende 5.1 und dem Bremsring 11 ausgebildete Stützlagerung 24 wird in diesem Ausführungsbeispiel durch ein Wälzlager gebildet, dass zwischen einem Wellenabsatz 28 der Pumpenwelle 5 und einem Gehäuseabsatz 29 des Wellengehäuses 1.4 angeordnet ist. Über den Wellenabsatz 28 und dem Gehäuseabsatz 29 lassen sich vorteilhaft axial wirkende Kräfte an der Pumpenwelle 5 aufnehmen. Ebenso werden die von außen über das Kupplungsende 5.1 der Pumpenwelle 5 angreifenden Kräfte durch die Stützlagerung 24 abgefangen und nicht ins Innere des Pumpengehäuses 1 geleitet.The trained between the coupling end 5.1 and the brake ring 11 support bearing 24 is formed in this embodiment by a rolling bearing that is disposed between a shaft shoulder 28 of the pump shaft 5 and a housing shoulder 29 of the shaft housing 1.4. About the shaft shoulder 28 and the housing shoulder 29 can advantageously record axially acting forces on the pump shaft 5. Likewise, the forces acting from the outside over the coupling end 5.1 of the pump shaft 5 forces are intercepted by the support bearing 24 and not directed into the interior of the pump housing 1.

Das Kupplungsende 5.1 der Pumpenwelle 5 ist identisch zu dem Ausführungsbeispiel nach Fig. 1 ausgeführt und trägt die Kupplungshülse 9. Hierbei ist die Kupplungshülse 9 in der Aufnahmebohrung 10 des Wellengehäuses 1.4 durch eine Lagerhülse 30 gehalten, die gleichzeitig eine Lagerstelle für eine kuppelbare Antriebswelle darstellt. In der Antriebswelle lässt sich über die Aufnahmeöffnung 13 am Ende des Wellengehäuses 1.4 einführen und über die Kupplungshülse 9 mit der Pumpenwelle 5 verbinden.The coupling end 5.1 of the pump shaft 5 is identical to the embodiment according to Fig. 1 Here, the coupling sleeve 9 is held in the receiving bore 10 of the shaft housing 1.4 by a bearing sleeve 30, which simultaneously represents a bearing point for a detachable drive shaft. In the drive shaft can be introduced via the receiving opening 13 at the end of the shaft housing 1.4 and connect via the coupling sleeve 9 with the pump shaft 5.

BezugszeichenlisteLIST OF REFERENCE NUMBERS

11
Pumpengehäusepump housing
1.11.1
äußere Gehäuseplatteouter housing plate
1.21.2
äußere Gehäuseplatteouter housing plate
1.31.3
mittlere Gehäuseplattemiddle housing plate
1.41.4
Wellengehäuseshaft housing
1.51.5
Dichtringseal
1.61.6
Dichtringseal
22
Pumpeneinlasspump inlet
33
Zahnrad (mitlaufend)Gear (running)
44
Zahnrad (getrieben)Gear (driven)
55
Pumpenwellepump shaft
5.15.1
Kupplungsendecoupling end
5.25.2
Profilierungprofiling
5.35.3
Reibflächefriction surface
66
Lagerwellebearing shaft
6.1, 6.26.1, 6.2
Lagerbuchsebearing bush
7.1, 7.27.1, 7.2
Lagerbohrungbearing bore
8.1, 8.28.1, 8.2
Lagerbuchsebearing bush
99
Kupplungshülsecoupling sleeve
1010
Aufnahmebohrunglocation hole
1111
Bremsringbrake ring
11.111.1
Bremsflächebrake surface
1212
Sicherungsringcirclip
1313
Aufnahmeöffnungreceiving opening
1414
WellendichtringShaft seal
1515
Trägerringsupport ring
1616
Bremssegmentebrake segments
16.116.1
TeilbremsflächePartial braking surface
1717
Federringspring washer
1818
Lagerzapfenpivot
1919
Zapfenbohrungpin hole
2020
Dichtringseal
2121
Verbindungsmittelconnecting means
22.1, 22.222.1, 22.2
O-RingO-ring
2323
Spülkanalirrigation channel
2424
Stützlagerungstorage support
2525
Dichtlippesealing lip
2626
Ringraumannulus
2727
Kanalchannel
2828
Wellenabsatzshaft shoulder
2929
Gehäuseabsatzhousing shoulder
3030
Lagerhülsebearing sleeve
3131
Aussparungrecess

Claims (10)

  1. A gear pump having numerous gear wheels (3, 4), that engage with one another, for the conveyance of a medium, which are contained in a rotatable manner in a pump housing (1) and having a pump shaft (5) for driving one of the gear wheels (4), wherein the pump shaft (5) can be coupled to a drive unit by means of a coupling end (5.1), characterized in that a brake ring (11) is disposed on the circumference of the pump shaft (5), which acts on a friction surface (5.3) of the pump shaft (5) or on a friction surface of the pump housing (1) with at least one brake surface (11.1).
  2. The gear pump according to Claim 1, characterized in that the brake ring (11) is retained in the pump housing (1.4) such that it cannot rotate, and that the brake surface (11.1) is formed on an inner circumference of the brake ring (11).
  3. The gear pump according to Claim 2, characterized in that the friction surface (5.3) of the pump shaft (5) is an encircling girthed area on the circumference, the outer diameter of which is greater than the inner diameter of the brake ring (11).
  4. The gear pump according to Claim 2 or 3, characterized in that the brake ring (11) has numerous brake segments (16) evenly distributed on the inner circumference, which each form a sub-brake surface (16.1).
  5. The gear pump according to Claim 4, characterized in that the brake segments (16) extending axially in the lateral direction are molded on a carrier ring to create a component, and that the brake segments (16) are held on the circumference of the pump shaft (5) by means of an encompassing snap ring (17).
  6. The gear pump according to one of the Claims 1 - 5, characterized in that the pump housing (1) contains numerous housing plates (1.1, 1.2, 1.3) and a shaft housing (1.4), wherein the pump shaft (5) is supported in two external housing plates (1.1, 1.2) and extends with the coupling end (5.1) into the shaft housing (1.4), and wherein the brake ring (11) is disposed on a shaft section of the pump shaft (5) within the shaft housing (1.4).
  7. The gear pump according to Claim 6, characterized in that within the housing plates (1.1, 1.2, 1.3) and/or the shaft housing (1.4), a shaft gasket (14) is provided on the pump shaft (5), dedicated to a shaft section of the pump shaft (5) between a bearing (7.2, 8.2) and the brake ring (11).
  8. The gear pump according to Claim 6 or 7, characterized in that within the shaft housing (1.4) a support bearing (24) is formed for the radial and axial support of the pump shaft (5), dedicated to a shaft section of the pump shaft (5) between the brake ring (11) and the coupling end (5.1).
  9. The gear pump according to one of the Claims 1 - 8, characterized in that the brake ring (11) has an encircling sealing lip (25) at a spacing to the brake surface (1.1) for sealing purposes, which lies against the circumference of the pump shaft (5).
  10. The gear pump according to Claim 9, characterized in that the brake ring (11) and the shaft gasket (14) form an annular space (26) between them on the circumference of the pump shaft (5) and that the annular space (26) can be filled with a sealing liquid.
EP20110709925 2010-03-25 2011-03-18 Gear pump Active EP2550456B1 (en)

Applications Claiming Priority (2)

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DE102010012653A DE102010012653A1 (en) 2010-03-25 2010-03-25 gear pump
PCT/EP2011/054135 WO2011117154A2 (en) 2010-03-25 2011-03-18 Gear pump

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EP2550456A2 EP2550456A2 (en) 2013-01-30
EP2550456B1 true EP2550456B1 (en) 2015-05-06

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US (1) US9416781B2 (en)
EP (1) EP2550456B1 (en)
KR (1) KR101762989B1 (en)
CN (1) CN103097731B (en)
DE (1) DE102010012653A1 (en)
ES (1) ES2540097T3 (en)
MX (1) MX2012010497A (en)
RU (1) RU2530692C2 (en)
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RU2583197C1 (en) * 2015-04-07 2016-05-10 Акционерное общество "Каменскволокно" (АО "Каменскволокно") Metering gear pump
CN105298705B (en) * 2015-10-23 2017-11-24 北京航科发动机控制系统科技有限公司 A kind of method for ensureing that bearing and bushing fasten by dynamometry
CN106481553A (en) * 2016-11-11 2017-03-08 温州大学 A kind of damping brake structure of external gear rotary pump
DE102022000385A1 (en) 2022-02-01 2023-08-03 Oerlikon Textile Gmbh & Co. Kg External gear pump with shaft seal

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PT2122175E (en) 2007-03-20 2015-11-12 Oerlikon Textile Gmbh & Co Kg Gear wheel pump

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WO2011117154A2 (en) 2011-09-29
CN103097731A (en) 2013-05-08
CN103097731B (en) 2016-03-30
US20130034463A1 (en) 2013-02-07
RU2012145177A (en) 2014-04-27
RU2530692C2 (en) 2014-10-10
KR20130009998A (en) 2013-01-24
ZA201206874B (en) 2013-08-28
WO2011117154A3 (en) 2013-05-02
DE102010012653A1 (en) 2011-09-29
EP2550456A2 (en) 2013-01-30
KR101762989B1 (en) 2017-07-28
ES2540097T3 (en) 2015-07-08
MX2012010497A (en) 2012-10-15
US9416781B2 (en) 2016-08-16

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