WO2015082257A1 - Zahnradpumpe - Google Patents
Zahnradpumpe Download PDFInfo
- Publication number
- WO2015082257A1 WO2015082257A1 PCT/EP2014/075525 EP2014075525W WO2015082257A1 WO 2015082257 A1 WO2015082257 A1 WO 2015082257A1 EP 2014075525 W EP2014075525 W EP 2014075525W WO 2015082257 A1 WO2015082257 A1 WO 2015082257A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- bearing
- gear
- contact surface
- bearing bush
- gear pump
- Prior art date
Links
- 238000005461 lubrication Methods 0.000 claims abstract description 29
- 230000001050 lubricating effect Effects 0.000 claims description 14
- 230000002093 peripheral effect Effects 0.000 abstract 1
- 238000005086 pumping Methods 0.000 abstract 1
- 239000012530 fluid Substances 0.000 description 10
- 238000009826 distribution Methods 0.000 description 6
- 238000011161 development Methods 0.000 description 5
- 230000018109 developmental process Effects 0.000 description 5
- 229920003023 plastic Polymers 0.000 description 4
- 239000004033 plastic Substances 0.000 description 4
- 230000007704 transition Effects 0.000 description 3
- 239000000155 melt Substances 0.000 description 2
- 238000007789 sealing Methods 0.000 description 2
- 238000005336 cracking Methods 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000006116 polymerization reaction Methods 0.000 description 1
- 230000001902 propagating effect Effects 0.000 description 1
- 230000010349 pulsation Effects 0.000 description 1
- 238000003860 storage Methods 0.000 description 1
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
- F04C2/18—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with similar tooth forms
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C13/00—Adaptations of machines or pumps for special use, e.g. for extremely high pressures
- F04C13/001—Pumps for particular liquids
- F04C13/002—Pumps for particular liquids for homogeneous viscous liquids
-
- 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
- F04C15/0088—Lubrication
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/084—Toothed wheels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2/00—Rotary-piston machines or pumps
- F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/086—Carter
Definitions
- the invention relates to a gear pump for conveying a highly viscous pumped medium according to the preamble of claim 1.
- gear pumps are preferably used to convey plastic melts.
- the gear pumps can be designed as so-called booster pumps for pressure increase in a polymerization process or as so-called extruder pumps in an extrusion process.
- Such gear pumps are thus subject to high requirements in terms of operating parameters such as temperatures and differential pressures.
- the highly viscous fluid is also usually used to lubricate the sliding bearings within the gear pump.
- it is generally customary to keep the bearing gaps and in particular the gaps formed at the ends of the gears as small as possible.
- one or more lubrication pockets for receiving the Födermediums are usually formed on the contact surface of the housing or a bushing.
- Such a gear pump is known for example from EP 1 291 526 A2.
- a gear pair is rotatably mounted within a housing.
- One of the gears is equipped with a connected to the drive shaft, which is rotatably mounted in the housing by two arranged respectively to the end faces of the gear bearing bushes.
- the driven gear is held via a bearing journal in two oppositely arranged bearing bushes in the housing, wherein the bearing bushes of the drive shaft and the bearing bushes of the journal support each other directly in a tooth engagement region of the gears.
- Each bushing forms opposite to a front side of the gear a contact surface on which the gear is supported.
- a plurality of radially aligned lubrication pockets which extend as a depression over the entire radial length of the contact surface, are embodied on the contact surface distributed over the circumference.
- the fluid can be passed directly from a bearing gap of the drive shaft in the lubrication pockets.
- the known gear pump has to distribute the medium at the contact surface on a stepped recess, so that in particular in the central region of the contact surface, a larger amount of the fluid is held for the purpose of lubrication.
- such lubrication pockets basically have the problem that no over the entire contact surface propagating distribution of the fluid adjusted for the purpose of lubrication.
- the lubricating pocket is formed on the contact surface by a radially and axially limited recess which is covered by an opposite end face of the gear and that a foot end of the recess via an opposite Umlaufkehlung on the gear with a bearing gap between the Drive shaft and the bearing bush is connected.
- the invention has the particular advantage that the rotational movement of the gear is used to obtain a continuous flow of the medium to be conveyed from the bearing gap between the drive shaft and the bearing bush to the lubricating pocket.
- a Umlaufkehlung is formed in the transition region between the drive shaft and the gear on the gear, extending in the radial direction on the front side of the gear extends to the foot of the recess at the contact surface.
- the gearwheel and the drive shaft are preferably formed in one piece to form a pinion shaft.
- the circulation is formed by an undercut in the pinion shaft.
- a distribution over the entire contact surface of the pumped medium is required for lubrication of the end face of the gear.
- the development of the invention has proven particularly useful in which the recess is diamond-shaped at the contact surface of the bearing bush and in the central region has a maximum depth of 0.15 mm to 0.4 mm.
- This particular wedge-shaped transition is preferably also formed on a head end of the depression opposite the foot end, so that the head end of the depression has an inclination in an angular range between 2 ° to 10 ° relative to the contact surface of the bearing bush. It is essential here that the dimensions of the lubrication pocket produced by the recess are substantially completely covered by the end face of the toothed wheel in order to ensure the pressure build-up and the distribution of the pumped medium.
- the development of the invention is preferably carried out, in which a plurality of depressions distributed on a pitch circle are formed on the contact surface of the bearing bush.
- the lubrication pockets can be made relatively small, in order nevertheless to lubricate the entire contact surface.
- the development of the invention is provided in which at least one lubrication groove is formed on the contact surface of the bearing bush, which connects a pressure chamber with the bearing gap between the drive shaft and the bearing bush. So can be realized within the bearing gap between the drive shaft and the bearing bush, a pressure gradient, which is a continuous Melt flow favors. As a result, fresh melt continuously reaches the area of the lubrication pockets.
- the lubrication groove on the contact surface of the bearing bush is preferably formed in the region of a pressure relief groove on the bearing bush, which is realized in a tooth engagement region of the toothed wheels on the bearing bush to reduce pressure pulsations.
- the bearing bush in the teeth tearing region of the gears cooperates with a storage journal for a bearing journal adjacent bush, so that a relief chamber is formed by a further Druckentlastungsnut the adjacent bearing bush between the bushings, which is connected to the Zahnwaitvolumen in the meshing region and leads to a desired Druckpulsationsminderung ,
- the development of the invention is particularly advantageous, in which a further bearing bush for supporting the drive shaft and / or for supporting the bearing journal has identically formed recesses on a contact surface opposite the gear wheel.
- a further bearing bush for supporting the drive shaft and / or for supporting the bearing journal has identically formed recesses on a contact surface opposite the gear wheel.
- FIG. 1 shows schematically a cross-sectional view of a first embodiment of the inventive gear pump
- FIG. 2 is a schematic plan view of a contact surface of a bearing bush of the embodiment of FIG. 1
- FIG. 3 schematically shows a detail of the cross-sectional view of the embodiment of FIG. 1.
- Fig. 4 shows schematically a cross-sectional view of another embodiment of the gear pump according to the invention
- Fig. 5 shows schematically a detail of the cross-sectional view of the embodiment of Fig. 4
- a first embodiment of the gear pump according to the invention is shown in a cross-sectional view.
- the embodiment has a multi-part housing 1, which consists of a front plate 1.1, an intermediate plate 1.2 and a back plate 1.3.
- the plates 1.1, 1.2 and 1.3 are pressure-tightly connected.
- a gear pair 2 is arranged within the intermediate plate 1.2.
- the gear pair 2 consists of a driving gear 2.1 and a driven gear 2.2, which cooperate in a tooth meshing zone 7 for conveying a highly viscous conveying medium preferably for conveying a plastic melt.
- the driving gear 2.1 is rotatably connected to a drive shaft 3.
- the drive shaft 3 is slidably mounted in two arranged on both sides of the gear 2.1 bushings 4.1 and 4.2.
- the drive shaft 3 penetrates the front panel 1.1 and is coupled to a drive, not shown here with a free end. Between the front plate 1.1 and the drive shaft 3, a shaft seal 8 is arranged.
- the driven gear 2.2 is rotatably connected to a bearing pin 5, which is rotatably mounted with its ends on both sides of the gear 2.2 in each case a bearing bush 6.1 and 6.2 slidably.
- the bearing bushes 4.1 and 4.2 of the drive shaft 3 and the bearing bushes 6.1 and 6.2 of the journal 5 each form a contact surface with respect to the gears 2.1 and 2.2, wherein in the meshing zone 7 a Dichtfu- 9 formed between the bearing bushes 4.1 and 6.1 and 4.2 and 6.2 is.
- FIG. 2 shows a schematic sectional position with a top view of the bearing bushes 4.1 and 6.1.
- the bearing bush 4.1 for supporting the drive shaft 3 is held in the intermediate plate 1.2 of the housing 1.
- the bearing bush 4.1 forms together with the drive shaft 3 a bearing gap 16.1.
- the bearing bush 4.1 has an outer diameter which is equal to or greater than an outer diameter of the driving gear 2.1. Only in the tooth engagement region 7, the bearing bush 4.1 on a flattening, which cooperates with an opposite flattening of the bearing bush 6.1 and forms the sealing joint 9.
- the position bushing 6.1 of the journal 5 is held in the same plane in the intermediate plate 1.2 and forms with the bearing pin 5 a bearing gap 16.2.
- the sealing joint 9 formed between the bearing bushes 4.1 and 6.1 separates in the housing 1 a pressure chamber 19 from an opposite suction chamber 20.
- the suction chamber 20 is connected to a pump inlet not shown here and the pressure chamber 19 with a pump outlet also not shown here.
- the pressure chamber 19 is extended in the tooth engagement zone 7 by a discharge chamber 18, which is formed by mirror-symmetrical Druckentlasungsnuten 17.1 and 17.2 in the contact surfaces 10.1 and 10.2 of the bearing bushes 4.1 and 6.1.
- the relief chamber 18 extends in a sub-region of the meshing zone 7 of the gears 2.1 and 2.2, in which a compressed tooth volume occurs. This can be impulsive flow rates and avoid the associated pressure fluctuations.
- the bearing bushing 6.1 for supporting the journal 5 also has a lubrication groove 21.2, the Druckentlastungsnut 17.2 with the bearing gap
- each bearing bushes 4.1, 4.2, 6.1 and 6.2 each have an end face of the gears 2.1 and 2.2.
- the contact surface 10.1 on the bearing bush 4.1 cooperates with an end face 23.1 of the gear 2.1.
- an end face 23.2 of the gear 2.2 cooperates with the contact surface 10.2 of the bearing bush 6.1.
- a plurality of lubrication pockets 11.1 are formed on the contact surface 10.1 distributed on a pitch circle 24.
- the arrangement and distribution of the lubricating pockets 11.1 is apparent in particular from the illustration in FIG.
- the lubrication pockets 11.1 are in this case formed by a radially and axially limited recess 12, which is placed on the contact surface 10.1 such that by the opposite end face 23.1 of the gear 2.1 complete coverage is ensured.
- FIG. 3 shows a section of the cross-sectional view from FIG. 1. The detail shows a cross section of the lubricating pocket 11.1, which extends between the bearing bush 4.1 and the gear 2.1.
- the recess 12 in a central region to a maximum depth, which is designated by the reference symbol T.
- the recess 12 extends between a foot end 13 and an opposite head end 14.
- Als Foot 13 is hereby referred to the end of the recess 2, which faces the inner diameter of the bearing bush 4.1.
- the head end 14 is thus the end of the recess 12, which faces an outer diameter of the bearing bush 4.1.
- the recess 12 is designed to be wedge-shaped at the foot end 13 and the head end 14, so that the recess 12 at the foot end 13 with respect to the contact surface 10.1 has an inclination at an angle ß.
- the opposite head end 14 of the recess 12 is formed by an inclination, which forms an angle ⁇ with the contact surface 10.1.
- the angle ⁇ and the angle ß is preferably carried out identically and is in an angular range between 2 ° to max. 10 °.
- a depth T in the range of 0.15 mm to 0.4 mm lead the wedge-shaped ends 13 and 14 of the recess 12 in connection with a sliding movement of the end face 23.1 of the gear 2.1 to a structure of a lubricating pressure, so that in the Deepening 12 held conveyed medium is pressed into a gap formed between the end face 23.1 of the gear 2.1 and the contact surface 10.1 of the bearing bush 4.1.
- a circulation groove 22 is formed in the transition region between the drive shaft 3 and the gearwheel 2.1.
- the Umlaufkehlung 22 is performed on the front side 23.1 of the gear 2.1 such that the foot end 13 of the recess 12 is partially covered by the Umlaufkehlung 22 so that its connection between the recess 12 and the bearing gap 16.1 arises.
- the circumferential groove 22 is formed circumferentially, so that adjacent lubricating bags 11.1 at the contact surface 4.1 are also continuously fed with the fluid from the bearing gap 16.1.
- the diamond-shaped lubrication pockets 11.1 are identically designed on the contact surface 4.1.
- the description of FIG. 3 also applies to the adjacent lubrication pockets 11.1.
- the lubrication pockets 11.2 are identical to the contact surface 10.2 of the bearing bush 6.1.
- all sliding pairings which arise between the bearing bushes 4.1, 4.2, 6.1 and 6.2 and the drive shaft 3, the bearing journal 5 and the gear pair 2 are continuously lubricated with the conveying medium. Due to the wedge-shaped design of the lubrication pockets on the contact surfaces of the bearing bushes, the friction pairing between the gear wheels and the bearing bushes, in particular, is kept wear-resistant even with highly viscous conveying media.
- FIGS. 4 and 5 show a further exemplary embodiment of a possible variant of the gear pump according to the invention.
- FIG. 4 schematically shows a cross-sectional view of the exemplary embodiment
- FIG. 5 shows a section of the illustration from FIG. 4 in the region of a lubricating pocket.
- the embodiment of FIGS. 4 and 5 is substantially identical to the aforementioned embodiment, so that at this point reference is made to the above description and only the differences will be explained.
- the gear 2.1 and the drive shaft 3 are made in one piece and formed by a pinion shaft 26.
- the pinion shaft 26 is rotatably supported in the housing 1 by the bearing bushes 4.1 and 4.2 and protrudes with a free end of the housing 1 out.
- the driven gear 2.2 of the gear pair 2 is also connected together with the bearing pin 5 to a one-piece pinion pin 27.
- the pinion pin 27 is slidably mounted in the housing 1 through the bearing bushes 6.1 and 6.2.
- the bushings 4.1, 4.2, 6.1 and 6.2 are identical to the aforementioned embodiment, so that no further explanation takes place at this point.
- an undercut 25 is formed on the diameter step of the pinion shaft 26, which establishes a connection between a bearing gap 16. 1 and the recess 12.
- the position gap 16.1 is formed between the position sleeve 4.1 and the pinion shaft 26.
- the undercut 25 on the pinion shaft 26 can thus be advantageously used to receive the conveying medium flowing into the bearing gap 16.1 and to feed it to the base end 13 of the depression 12. In that regard, the lubricating pocket 11.1 can be fed continuously.
- the invention is therefore independent of whether a pinion shaft or separate gears are used on the gear pump.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112014005509.3T DE112014005509A5 (de) | 2013-12-03 | 2014-11-25 | Zahnradpumpe |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102013020162 | 2013-12-03 | ||
DE102013020162.4 | 2013-12-03 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2015082257A1 true WO2015082257A1 (de) | 2015-06-11 |
Family
ID=52000823
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2014/075525 WO2015082257A1 (de) | 2013-12-03 | 2014-11-25 | Zahnradpumpe |
Country Status (2)
Country | Link |
---|---|
DE (1) | DE112014005509A5 (de) |
WO (1) | WO2015082257A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11940094B2 (en) | 2017-04-27 | 2024-03-26 | Hove A/S | Central lubricating station |
Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB883356A (en) * | 1959-04-24 | 1961-11-29 | Thompson Ramo Wooldridge Inc | Improvements in or relating to pumps |
JPH11218084A (ja) * | 1998-02-02 | 1999-08-10 | Koyo Seiko Co Ltd | ギヤポンプ及びこれを用いた動力舵取装置 |
EP1291526A2 (de) * | 2001-09-07 | 2003-03-12 | Mario Antonio Morselli | Zahnradförderpumpe |
DE102009037199A1 (de) * | 2009-08-12 | 2011-02-17 | Robert Bosch Gmbh | Hydraulische Zahnradmaschine |
-
2014
- 2014-11-25 WO PCT/EP2014/075525 patent/WO2015082257A1/de active Application Filing
- 2014-11-25 DE DE112014005509.3T patent/DE112014005509A5/de active Pending
Patent Citations (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
GB883356A (en) * | 1959-04-24 | 1961-11-29 | Thompson Ramo Wooldridge Inc | Improvements in or relating to pumps |
JPH11218084A (ja) * | 1998-02-02 | 1999-08-10 | Koyo Seiko Co Ltd | ギヤポンプ及びこれを用いた動力舵取装置 |
EP1291526A2 (de) * | 2001-09-07 | 2003-03-12 | Mario Antonio Morselli | Zahnradförderpumpe |
DE102009037199A1 (de) * | 2009-08-12 | 2011-02-17 | Robert Bosch Gmbh | Hydraulische Zahnradmaschine |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US11940094B2 (en) | 2017-04-27 | 2024-03-26 | Hove A/S | Central lubricating station |
Also Published As
Publication number | Publication date |
---|---|
DE112014005509A5 (de) | 2016-09-29 |
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