EP3198145A1 - Pump unit - Google Patents
Pump unitInfo
- Publication number
- EP3198145A1 EP3198145A1 EP15744157.7A EP15744157A EP3198145A1 EP 3198145 A1 EP3198145 A1 EP 3198145A1 EP 15744157 A EP15744157 A EP 15744157A EP 3198145 A1 EP3198145 A1 EP 3198145A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- drive shaft
- bearing
- rotor
- sliding bearing
- sliding
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 230000002093 peripheral effect Effects 0.000 claims description 17
- 238000004804 winding Methods 0.000 claims description 8
- 239000000463 material Substances 0.000 claims description 6
- 239000012530 fluid Substances 0.000 description 4
- 238000002347 injection Methods 0.000 description 3
- 239000007924 injection Substances 0.000 description 3
- 238000001746 injection moulding Methods 0.000 description 3
- 239000006247 magnetic powder Substances 0.000 description 2
- 229910000976 Electrical steel Inorganic materials 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 239000011248 coating agent Substances 0.000 description 1
- 238000000576 coating method Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 238000011161 development Methods 0.000 description 1
- 230000018109 developmental process Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000003475 lamination 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
- F04C2/082—Details specially related to intermeshing engagement type machines or pumps
- F04C2/084—Toothed wheels
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
- F01C3/00—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members
- F01C3/06—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees
- F01C3/08—Rotary-piston machines or engines with non-parallel axes of movement of co-operating members the axes being arranged otherwise than at an angle of 90 degrees 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
- F04C3/00—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type
- F04C3/06—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees
- F04C3/08—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C3/085—Rotary-piston machines or pumps, with non-parallel axes of movement of co-operating members, e.g. of screw type the axes being arranged otherwise than at an angle of 90 degrees of intermeshing engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing the axes of cooperating members being on the same plane
-
- 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
- F04C2240/50—Bearings
- F04C2240/56—Bearing bushings or details thereof
-
- 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
- F04C2240/60—Shafts
Definitions
- Bearing portion arranged in a second sliding bearing.
- larger forces act on the first sliding bearing than on the second sliding bearing, since the hydraulic pressure forces occurring in the working chambers of the delivery unit act on the drive shaft via the rotor and the oblique sliding surface and must be absorbed predominantly by the first sliding bearing.
- Load capacity of the rotor facing the sliding bearing is limited to a predetermined working pressure in the delivery unit.
- Main claim has the advantage that the carrying capacity of the rotor facing the first slide bearing is increased compared to the carrying capacity of the second sliding bearing by the diameter of the first bearing portion of the drive shaft and the first sliding bearing is made larger than the diameter of the second bearing portion and the second sliding bearing ,
- the delivery unit seen by the inventive design in the axial direction of the drive shaft to be built shorter.
- Due to the different diameters of the two bearing portions is at least one between the first bearing portion and the second bearing portion
- the drive shaft is thereby particularly easily demoulded from an injection mold of an injection molding machine.
- an anchor portion is provided on the drive shaft between the two bearing sections, which at its periphery
- Drive shaft surrounds annular. In this way, a cost-effective electric drive is realized, whose armature is integrated in the drive shaft. It is particularly advantageous if the anchor portion has a diameter in the region between the diameter of the first bearing portion and the
- Diameter of the second bearing section is. In this way, two stepped heels are formed between the two bearing sections.
- the diameter of the anchor portion for each new design in the range between the diameters of the first and the second bearing portion can be optimally selected.
- the efficiency of the electric motor can be optimized in a simple manner.
- first sliding bearing and the second sliding bearing are each arranged on one end face of the stator, since the two sliding bearings can be integrated in this way in a circumferential wall of the housing of the delivery unit and thus can be produced inexpensively. Moreover, it is advantageous if in the circumferential wall of the housing between the two plain bearings two stages are formed, which separate the two plain bearings of a stator, since the housing is particularly easily removed from an injection mold of an injection molding machine in this way.
- stator is integrated with its electrical winding in the material of the peripheral wall of the housing of the delivery unit, since the stator and its electrical winding are sealed in this way against the fluid.
- the seal is made by the stator is encapsulated on its front sides and also on its inner and outer peripheral side of plastic.
- stator is arranged in the circumferential wall of the housing in the axial direction between the first sliding bearing and the second slide bearing, since in this way an electric drive with a short axial length can be realized.
- peripheral wall of the housing is made of plastic. In this way, the housing can be produced very inexpensively in an injection molding process.
- the delivery unit for example a pump or a compressor, has a housing 1, in which a drive shaft 2 and a driven by the drive shaft 2, rotatably arranged rotor 3 is provided.
- the drive shaft 2 has on an end facing the rotor 3 an inclined sliding surface 4, which rotates the rotor 3 with its rotor axis 5 upon rotation of the drive shaft 2 about a drive axis 6 of Drive shaft 2 tumble.
- the rotor 3 has on its side facing the drive shaft 2 a co-operating with the oblique sliding surface 4 sliding surface 8 and facing away from the drive shaft 2 end face a toothing 9, which meshes with a trained example of the housing 1 10 teeth.
- the inclined sliding surface 4 and the sliding surface 8 are formed, for example, as flat surfaces. Between the teeth 9 of the rotor 3 and the toothing 10 of the housing 1 working spaces 11 are formed, which via an input 12 of the
- Delivery units can be filled and emptied via an output 13 of the delivery unit.
- the toothing 9 of the rotor 3 and the toothing 10 of the housing 1 is designed, for example, as a cycloidal toothing, but may also be a different toothing.
- the delivery unit works according to the displacement principle, so that the fluid is sucked in self-priming via the input 12 into the working chambers 11 and discharged from the latter via the output 13.
- the drive shaft 1 has a through-passage 14 to transport fluid from the inlet 12 into the working spaces 11 or out of these to the outlet 13. Which opening 12, 13 of the delivery unit is input or output depends on the direction of rotation of the rotor 3.
- the portion of the housing 1, on which the toothing 10 is provided is designed for example as a separate housing cover 15, which closes another portion of the housing 1, which is for example cylindrical or cup-shaped.
- the drive shaft 2 has a first bearing section 18 facing the rotor 3 and a second bearing section 19 facing away from the rotor 3, wherein the first bearing section 18 of the drive shaft 2 is arranged in a first sliding bearing 20 and the second bearing section 19 is arranged in a second sliding bearing 21.
- the diameter of the first bearing section 18 of the drive shaft 2 and of the first sliding bearing 20 is made larger than the diameter of the second bearing section 19 and the second sliding bearing 21.
- the oblique sliding surface 4 adjoins the end face directly to the first bearing portion 18, namely substantially continuously or at least without extension of the diameter of the drive shaft 2.
- an anchor portion 22 is provided the one at its periphery Permanent magnets 23 which cooperate with an electrical winding 26 of an electric stator 27 which surrounds the armature portion 22 of the drive shaft 2 in an annular manner. In this way, a cost-effective electric motor is formed.
- the stator 27 is formed for example by a package of stacked laminations of so-called electrical steel.
- the permanent magnets 23 are arranged in at least one receptacle 25 of the drive shaft 2.
- Permanent magnets 23 may be individual magnets or on a single
- Magnet ring be formed is embedded in the material magnetic powder.
- the magnetic ring may be made of a plastic as a base material in which the magnetic powder is distributed.
- the arranged in the receptacle 25 permanent magnets 23 may be compared to the fluid of the
- the permanent magnets 23 may be arranged eccentrically on the drive shaft 2 with respect to the stator 27 and in the direction of the drive shaft 6 so that the drive shaft 2 is pressed against the rotor 3 with a predetermined magnetic force.
- the permanent magnets 23 are arranged offset to the drive shaft 2 relative to a central arrangement with respect to the stator 27 in the direction away from the rotor 3.
- the anchor portion 22 of the drive shaft 2 has a diameter which is in the range between the diameter of the first bearing portion 18 and the diameter of the second bearing portion 19. In this way, two step-like shoulders 28 are formed between the two bearing sections 18, 19 of the drive shaft 2.
- the first sliding bearing 20 and the second sliding bearing 21 are arranged on different sides of the stator 27, for example, in each case on one of the end faces.
- the first sliding bearing 20 and the second sliding bearing 21 are on one of the drive shaft. 2
- the peripheral wall 29 of the housing 1 defines a space for receiving the drive shaft 2.
- the plain bearings 20,21 can through the
- Circumferential wall 29 itself formed or as a separate component, for example as a plain bearing bush, be arranged on the peripheral wall 29. According to the
- two stages 30 are provided in the peripheral wall 29 of the housing 1 between the two plain bearings 20,21, which separate the two plain bearings 20,21 of a stator 31, which formed of its diameter is that between the anchor portion 22 of the drive shaft 2 and the
- Stator region 31 of the housing 1 results in the smallest possible air gap.
- the electric stator 27 is integrated according to the embodiment with its electrical winding 26 in the material of the peripheral wall 29 of the housing 1, wherein the stator 27 disposed in the peripheral wall 29 of the housing 1 in the axial direction between the first sliding bearing 20 and the second sliding bearing 21 is.
- the integration of the stator 27 in the peripheral wall 29 of the housing 1 is achieved by the stator 27 with its electrical winding 26 in the
- Circumferential wall 29 is cast with, that is completely or partially enclosed in the material of the peripheral wall 29.
- the peripheral wall 29 of the housing 1 is made of plastic and injection molded.
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102014219219.6A DE102014219219A1 (en) | 2014-09-24 | 2014-09-24 | delivery unit |
PCT/EP2015/066750 WO2016045817A1 (en) | 2014-09-24 | 2015-07-22 | Pump unit |
Publications (2)
Publication Number | Publication Date |
---|---|
EP3198145A1 true EP3198145A1 (en) | 2017-08-02 |
EP3198145B1 EP3198145B1 (en) | 2018-07-04 |
Family
ID=53761349
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP15744157.7A Active EP3198145B1 (en) | 2014-09-24 | 2015-07-22 | Pump unit |
Country Status (4)
Country | Link |
---|---|
US (1) | US10151312B2 (en) |
EP (1) | EP3198145B1 (en) |
DE (1) | DE102014219219A1 (en) |
WO (1) | WO2016045817A1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102017203521A1 (en) | 2017-03-03 | 2018-09-06 | Robert Bosch Gmbh | delivery unit |
DE102021103306A1 (en) | 2021-02-12 | 2022-08-18 | Kolektor Group D.O.O. | Hand-held hydraulic fluid device |
WO2023186297A1 (en) * | 2022-03-30 | 2023-10-05 | Pierburg Gmbh | Electric machine |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
ATE62325T1 (en) * | 1987-09-15 | 1991-04-15 | Bieri Pumpenbau Ag | CIRCULATION PUMP ESPECIALLY FOR HOT WATER SYSTEMS. |
US5508575A (en) * | 1994-01-27 | 1996-04-16 | Hr Textron Inc. | Direct drive servovalve having magnetically loaded bearing |
JP4516641B2 (en) | 1999-06-18 | 2010-08-04 | キヤノンアネルバ株式会社 | Fluid pressure feeder |
DE10254670A1 (en) * | 2002-11-22 | 2004-06-24 | Minebea Co., Ltd. | Electric motor for a pump drive |
DE102004044297A1 (en) | 2003-09-11 | 2005-05-04 | Cor Pumps & Compressors Ag | Rotating piston machine has electric motor installed in motor casing with rotor mounted on one side in motor casing and on other side in machine casing co-axially with driven component of machine's rotor |
US20050220641A1 (en) * | 2004-04-02 | 2005-10-06 | Denso Corporation | Fuel pump, fuel supply equipment using fuel pump and method for manufacturing fuel pump |
US8834140B2 (en) | 2004-05-25 | 2014-09-16 | Cor Pumps + Compressors Ag | Leakage loss flow control and associated media flow delivery assembly |
CN101960089B (en) * | 2007-03-13 | 2013-07-31 | 罗伯特·博世有限公司 | Pump or motor |
JP4483952B2 (en) * | 2008-01-29 | 2010-06-16 | 株式会社デンソー | Pump with motor |
EP2250375A4 (en) | 2008-10-23 | 2014-12-17 | Swashpump Technologies Ltd | Integrated pump for compressible fluids |
JP5727806B2 (en) * | 2010-02-26 | 2015-06-03 | 山洋電気株式会社 | Electrical cable connection structure and electrical equipment |
DE102010040758A1 (en) | 2010-09-14 | 2012-03-15 | Robert Bosch Gmbh | delivery unit |
US9624817B2 (en) * | 2012-03-09 | 2017-04-18 | Brose Fahrzeugteile GmbH & Co. Kommanditgesellschaft, Würzburg | Cooling fan module and adapter device therefor |
-
2014
- 2014-09-24 DE DE102014219219.6A patent/DE102014219219A1/en not_active Withdrawn
-
2015
- 2015-07-22 WO PCT/EP2015/066750 patent/WO2016045817A1/en active Application Filing
- 2015-07-22 EP EP15744157.7A patent/EP3198145B1/en active Active
- 2015-07-22 US US15/514,108 patent/US10151312B2/en active Active
Also Published As
Publication number | Publication date |
---|---|
US10151312B2 (en) | 2018-12-11 |
DE102014219219A1 (en) | 2016-03-24 |
WO2016045817A1 (en) | 2016-03-31 |
EP3198145B1 (en) | 2018-07-04 |
US20170292516A1 (en) | 2017-10-12 |
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