EP2550456B1 - Gear pump - Google Patents
Gear pump Download PDFInfo
- 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
Links
- 230000008878 coupling Effects 0.000 claims description 25
- 238000010168 coupling process Methods 0.000 claims description 25
- 238000005859 coupling reaction Methods 0.000 claims description 25
- 238000007789 sealing Methods 0.000 claims description 17
- 239000007788 liquid Substances 0.000 claims description 4
- 230000000717 retained effect Effects 0.000 claims 1
- 230000004888 barrier function Effects 0.000 description 6
- 238000011161 development Methods 0.000 description 6
- 230000018109 developmental process Effects 0.000 description 6
- 239000003973 paint Substances 0.000 description 5
- 239000012530 fluid Substances 0.000 description 4
- 239000000463 material Substances 0.000 description 3
- 230000008901 benefit Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000032683 aging Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 210000003746 feather Anatomy 0.000 description 1
- 230000009969 flowable effect Effects 0.000 description 1
- 238000011010 flushing procedure Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 230000002262 irrigation Effects 0.000 description 1
- 238000003973 irrigation Methods 0.000 description 1
- 239000004922 lacquer Substances 0.000 description 1
- 230000035515 penetration Effects 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 238000010926 purge Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 239000002904 solvent Substances 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
Images
Classifications
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- 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.
Landscapes
- 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
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
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
- 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
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
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
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
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
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
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
Bei dem in
Je nach Ausführung der Pumpe können unterschiedliche Ausführungsformen zur zusätzlichen Abbremsung der Pumpenwelle genutzt werden. So wäre bei dem Ausführungsbeispiel nach
In
Bei dem Ausführungsbeispiel nach
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
Zur weiteren Erläuterung des Bremsringes 11 wird neben der
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
Die Funktion des in
In
Bei dem Ausführungsbeispiel nach
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
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
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
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
Zur Erläuterung des in diesem Ausführungsbeispiel eingesetzten Bremsringes 11 wird zusätzlich zu der
Bei dem in
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
Das Kupplungsende 5.1 der Pumpenwelle 5 ist identisch zu dem Ausführungsbeispiel nach
- 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)
- 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).
- 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).
- 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).
- 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).
- 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).
- 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).
- 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).
- 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).
- 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).
- 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.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102010012653A DE102010012653A1 (en) | 2010-03-25 | 2010-03-25 | gear pump |
PCT/EP2011/054135 WO2011117154A2 (en) | 2010-03-25 | 2011-03-18 | Gear pump |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2550456A2 EP2550456A2 (en) | 2013-01-30 |
EP2550456B1 true EP2550456B1 (en) | 2015-05-06 |
Family
ID=44503740
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20110709925 Active EP2550456B1 (en) | 2010-03-25 | 2011-03-18 | Gear pump |
Country Status (10)
Country | Link |
---|---|
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) |
WO (1) | WO2011117154A2 (en) |
ZA (1) | ZA201206874B (en) |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102013215449A1 (en) * | 2013-08-06 | 2015-02-12 | Robert Bosch Gmbh | Coupling device for a metering pump |
WO2016026091A1 (en) * | 2014-08-19 | 2016-02-25 | 湖南机油泵股份有限公司 | Oil pump for internal combustion engine |
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 |
Family Cites Families (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2279775A (en) * | 1939-11-27 | 1942-04-14 | Mergenthaler Linotype Gmbh | Brake for revolving machine parts |
SU1435825A1 (en) * | 1987-03-11 | 1988-11-07 | Предприятие П/Я Ю-9796 | Vacuum pump |
US5299676A (en) | 1991-08-15 | 1994-04-05 | Ivg Australia Pty. Limited | Rotation check mechanism |
DE4408164C2 (en) * | 1994-03-11 | 2003-02-27 | Johann Spreitzer | Hydraulic clamping device for rotating driven shafts |
RU2109988C1 (en) * | 1996-03-26 | 1998-04-27 | Андрей Рудольфович Сплошнов | Rotary machine |
JPH10274171A (en) * | 1997-01-31 | 1998-10-13 | United Dominion Ind Inc | Constant positioned cleaning gear pump |
EP1164293B1 (en) | 2000-06-14 | 2006-09-13 | Saurer GmbH & Co. KG | Gear pump with a flushing system |
DE102004052558A1 (en) * | 2004-10-29 | 2006-05-04 | Saurer Gmbh & Co. Kg | gear pump |
DE102005059563A1 (en) | 2005-12-13 | 2007-06-14 | Dürr Systems GmbH | Dosing pump e.g. gear pump, for dosing liquid surface coating medium, has notch receiving sealing ring that forms static radial sealing at outer diameter of ring, where ring is sealed between outer diameter of ring and notch |
PT2122175E (en) | 2007-03-20 | 2015-11-12 | Oerlikon Textile Gmbh & Co Kg | Gear wheel pump |
-
2010
- 2010-03-25 DE DE102010012653A patent/DE102010012653A1/en not_active Withdrawn
-
2011
- 2011-03-18 EP EP20110709925 patent/EP2550456B1/en active Active
- 2011-03-18 CN CN201180015655.0A patent/CN103097731B/en active Active
- 2011-03-18 WO PCT/EP2011/054135 patent/WO2011117154A2/en active Application Filing
- 2011-03-18 KR KR1020127027972A patent/KR101762989B1/en active IP Right Grant
- 2011-03-18 MX MX2012010497A patent/MX2012010497A/en active IP Right Grant
- 2011-03-18 RU RU2012145177/06A patent/RU2530692C2/en active
- 2011-03-18 ES ES11709925.9T patent/ES2540097T3/en active Active
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2012
- 2012-09-13 ZA ZA2012/06874A patent/ZA201206874B/en unknown
- 2012-09-25 US US13/626,045 patent/US9416781B2/en active Active
Also Published As
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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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