WO2018114919A1 - Pompe à engrenages extérieurs pour système de récuperation de chaleur perdue - Google Patents

Pompe à engrenages extérieurs pour système de récuperation de chaleur perdue Download PDF

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Publication number
WO2018114919A1
WO2018114919A1 PCT/EP2017/083496 EP2017083496W WO2018114919A1 WO 2018114919 A1 WO2018114919 A1 WO 2018114919A1 EP 2017083496 W EP2017083496 W EP 2017083496W WO 2018114919 A1 WO2018114919 A1 WO 2018114919A1
Authority
WO
WIPO (PCT)
Prior art keywords
plate
external gear
shaft
gear pump
top plate
Prior art date
Application number
PCT/EP2017/083496
Other languages
German (de)
English (en)
Inventor
Guido Bredenfeld
Jakob Branczeisz
Matthias RIEDLE
Toni Jankowski
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2018114919A1 publication Critical patent/WO2018114919A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/08—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
    • F04C2/12—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
    • F04C2/14—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
    • 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

Definitions

  • the present invention relates to an external gear pump, in particular embodied as a feed fluid pump of a waste heat recovery system of an internal combustion engine.
  • Fluid delivery pumps are widely known from the prior art, for example as external gear pumps from the published patent application DE 10 2009 045 030 A1.
  • the external gear pump according to the invention has the advantage that it can be used for low-viscosity, poorly lubricating working media even at low operating pressures. Furthermore, the
  • External gear pump in particular for waste heat recovery systems of internal combustion engines.
  • the external gear pump has a housing.
  • the housing comprises a top plate, a bottom plate and a frame plate.
  • the frame plate is disposed between the top plate and the bottom plate.
  • a recess is formed as a working space.
  • a first gear arranged on a first shaft and a second gear arranged on a second shaft are meshed with each other.
  • the first shaft and the second shaft each protrude through both the top plate and the bottom plate.
  • a first sealing member is between the first shaft and the top plate
  • a second sealing member is between the first shaft and the bottom plate
  • a third sealing member is disposed between the second shaft and the top plate
  • a fourth sealing member is disposed between the second shaft and the bottom plate.
  • the external gear pump conveys a working medium which passes from the working space via leakage paths only up to the upper or lower plate arranged four sealing elements.
  • the more distant bearings of the waves thus no longer come into contact with the working fluid, but rather can even be lubricated with an advantageous lubricant, so that the tribological conditions in the
  • the strong can be so strong
  • the four sealing elements are each designed as a shaft seal. This is a simple, space-saving and cost-effective way of sealing between the waves and the top and bottom plate. Nevertheless, the shaft seal is also a very reliable sealing element.
  • the housing further comprises a lid and a bottom flange.
  • the lid is at the working space arranged side facing away from the top plate, and the bottom flange on the side facing away from the working space of the lower plate.
  • a sealing ring between the frame plate on the one hand and the top plate and the bottom plate on the other hand arranged for radial sealing of the working space. Due to the four sealing elements and the two sealing rings of the working space is thus sealed to the environment.
  • a further seal for a shaft drive is used, if one of the two shafts as
  • Drive shaft is formed and is guided out of the housing.
  • Gear wheels on the one hand and the top plate and the lower plate on the other hand arranged.
  • the Axialfeld plates serve the gears thus as thrust bearings, ideally a hydrodynamic lubrication gap between the end faces of the gears and the Axialfeldplatten is formed.
  • Axialfeldplatte on the one hand and the top plate and the lower plate on the other hand arranged.
  • the Axialfelddichtonne divide the spaces between the Axialfeldplatten on the one hand and the upper plate and the lower plate on the other hand each in a low-pressure chamber and a high-pressure chamber.
  • the external gear pump the faces of the gears are subject to locally different fluid pressures in the gap between the gears and the associated Axialfeldplatte. Accordingly, the gap would be greater in the region of higher pressures than in the region of lower pressures. This effect is counteracted by the back of the Axialfeld plates with a similar
  • the top plate, the frame plate and the lower plate are aligned by at least two dowel pins coaxially to each other.
  • the lid and the bottom flange are aligned by the at least two dowel pins coaxial with the other three plates.
  • a dial between the frame plate and the lower plate is arranged.
  • the height of the working space namely the height between the lower plate and the top plate is set.
  • This gap is preferably optimized to be a compromise solution of low wear and low leakage.
  • the following is a method for mounting an external gear pump with a shim claimed: First, the top plate, the frame plate and the two gears are positioned. Subsequently, the frame plate and the two gears are acted upon by the respective equivalent operating forces in the axial direction. In terms of forces, this means that an operating situation is set, preferably for the nominal pressure of the external gear pump. After that, under the
  • the height of the gears is greater than the thickness of the frame plate.
  • the shim is respect. Their thickness selected.
  • Waste heat recovery systems often use low viscosity, poorly lubricious working media. Therefore, the invention
  • the waste heat recovery system includes one
  • Expansion machine and a capacitor includes.
  • the feed fluid pump is designed as an external gear pump with the features described above.
  • Exploded view, showing only the essential area, 2 is a schematic sectional view through an external gear pump of the prior art
  • Fig. 3 is a schematic cross section through an inventive
  • Fig. 4 is a schematic cross section through an inventive
  • Fig. 5 shows a schematic cross section through a further embodiment of the external gear pump according to the invention, wherein only the essential areas are shown.
  • the external gear pump 1 shows an external gear pump 1 of the prior art in an exploded view.
  • the external gear pump 1 includes a
  • Pump housing 2 a cover 3 and a bottom flange 4.
  • the cover 3 and the bottom flange 4 are clamped together with the interposition of the pump housing 2 by four screws 5.
  • the pump housing 2, the lid 3 and the bottom flange 4 define a working space 6.
  • a first gear 1 1 and a second gear 12 are arranged in mesh with each other. Both gears 1 1, 12 have a certain number of teeth, each with a tooth width or gear width b.
  • the first gear 1 1 is mounted on a first shaft 21 and the second gear 12 on a first shaft 21 parallel to the second shaft 22.
  • the first shaft 21 serves as a drive shaft and is connected to a drive, not shown, for example, a crankshaft of an internal combustion engine , For this purpose, the first shaft 21 protrudes through the bottom flange. 4
  • the two shafts 21, 22 each protrude through their associated gear 1 1, 12 and are firmly connected to this, for example by one each Press Association. Alternatively, depending on a shaft and a gear can also be made in one piece. On both sides of the gears 1 1, 12, the shafts 21, 22 are mounted.
  • the storage is carried out by two bearing glasses 30, 40, wherein the
  • Bearing glasses 30, 40 are arranged in the working space 6: a bearing glasses 30 is disposed adjacent to the bottom flange 4 and another bearing glasses 40 adjacent to the lid 3. In both bearing glasses 30, 40 are each two bushings 9 pressed.
  • the bearing bushes 9 of the bearing glasses 30 store the two shafts 21, 22 on the drive side and the bearing bushes 9 of the other bearing glasses 40 on the opposite side of the gears 1 1, 12.
  • the bushings 9 thus form plain bearings for the two shafts 21, 22.
  • the two bearing bushes 9 can also be made in one piece with the bearing glasses 30.
  • the four bearing bushes 9 each have a radial bearing function and each form a plain bearing with their associated shaft 21, 22. Die
  • Axial bearing function is achieved by the two bearing glasses 30, 40:
  • the bearing glasses 30 on the front side a stop surface 31 and the other
  • Lagerbrille 40 frontally another stop surface 42. Both stop surfaces 31, 42 cooperate with two gears 1 1, 12 together.
  • the stop surface 31 supports both gears 1 1, 12 oriented in the axial direction to the bottom flange 4; the further stop surface 42 supports both gears 1 1, 12 oriented in the axial direction to the lid 3.
  • Both seals 28, 29 extend approximately annular over the circumference of the pump housing 28, 29 and are usually arranged in corresponding grooves.
  • a first Axialfelddichtung 18 is disposed between the bearing glasses 30 and the bottom flange 4, and between the other bearing glasses 40 and the lid 3, a second Axialfelddichtung 19 is arranged.
  • the two axial field seals 18, 19 constitute an axial bearing of the two bearing glasses 30, 40 within the pump housing 2.
  • the end faces or rear sides of the two bearing eyeglasses 30, 40 are characterized dependent on the angle of rotation either with the pressure level of the pressure range or with the pressure level of the suction range acted upon.
  • a delivery volume V of the working medium is thus conveyed to the housing wall of the pump housing 2 between the teeth of the two gears 1 1, 12 from the inlet 2 a to the outlet 2 b.
  • the delivery volume V corresponds to the volume delivered in nominal operation of the external gear pump 1, that is, the volume delivered in essential operating points.
  • External gear pump 1 with a low first pressure level - for example
  • Pressure level - for example, 40 bar - off.
  • Pressure range depends on the following flow topology, for example, from a throttle point.
  • the external gear pump 1 has a housing 2, which comprises a top plate 51, a bottom plate 52 and a frame plate 50.
  • the frame plate 50 is disposed between the top plate 51 and the bottom plate 52 and braced between them,
  • first gear 11 and arranged on a second shaft 22 second gear 12 are meshed with each other, as it corresponds to the usual operating principle of external gear pumps.
  • the first shaft 21 and the second shaft 22 each protrude through both the top plate 51 and the bottom plate 52.
  • the axial sealing of the working space 6 takes place at the respective passages of the two Shafts 21, 22 through the top plate 51 and lower plate 52.
  • the external gear pump 1 has four sealing elements 61, 62, 63, 64:
  • the four sealing elements 61, 62, 63, 64 are each designed as a shaft seal and each act in the radial direction with the shaft 21, 22 and the plate 51, 52 together.
  • Another sealing element 65 seals the housing 2 to the first shaft 21 designed as a drive shaft to the outside.
  • the first shaft 21 protrudes through the bottom flange 4 in order to be mechanically connected to a drive can.
  • the further sealing element 65 for example likewise designed as a shaft sealing ring, is arranged radially between the first shaft 21 and the bottom flange 4.
  • the housing 2 further comprises the lid 3 and the bottom flange 4.
  • the lid 3 cooperates with the top plate 51 and the bottom flange 4 with the bottom plate 52 together.
  • Bottom flange 4 are each arranged on the side facing away from the frame plate 50 side of top plate 51 and lower plate 52.
  • the four bearings 71, 72, 73, 74 for the two shafts 21, 22 are arranged:
  • a first bearing 71 is disposed in the lid 3 for supporting the first shaft 21.
  • a second bearing 72 is disposed in the bottom flange 4 for supporting the first shaft 21.
  • a third bearing 73 is disposed in the lid 3 for supporting the second shaft 22.
  • a fourth bearing 74 is disposed in the bottom flange 4 for supporting the second shaft 22.
  • the bearings 71, 72, 73, 74 can be designed as rolling or plain bearings.
  • the top plate 51, the frame plate 50, the lower plate 52, the cover 3 and the bottom flange 4 are aligned by two dowel pins 59 and clamped together by screws, wherein in each case a sealing ring 81, 82, 83, 84 between the plates 3, 51, 50 , 52, 4 is arranged to seal the housing 2 to the outside, in particular in the radial direction.
  • the holes for the dowel pins 59 must be provided symmetrically in all plates 3, 51, 50, 52, 4. As a result, in the end, especially the bearings 71, 72, 73, 74 are aligned exactly with the working space 6 formed in the frame plate 50, which
  • the frame plate 50 forms the radial seal of the working space 6 and preferably also includes the respective connection fittings to the low pressure and the high pressure; in the frame plate 50 thus also the inlet 2a and the outlet 2b are formed.
  • the internal geometry of the frame plate 50 forms the radial seal of the working space 6 and preferably also includes the respective connection fittings to the low pressure and the high pressure; in the frame plate 50 thus also the inlet 2a and the outlet 2b are formed.
  • Frame plate 50 should therefore be made very accurately in order to ensure the best possible radial seal to the tooth tips of the two gears 11, 12.
  • the two gap heights on both end sides of the gears 11, 12 are the same size.
  • the adjustment of the axial seal is made possible by a shim 53 which is disposed axially between the frame plate 50 and the lower plate 52. 4 shows a measurement of an axial distance s between the
  • Frame plate 50 and the gears 11, 12, wherein the determined axial Distance s represents the basis for the thickness of the shim 53 to be used.
  • the measurement is carried out in half assembled state of the external gear pump 1. There will be biasing forces on the
  • Frame plate 50 must be as large as the thickness of the gears 11, 12 plus the two axial gaps between the top plate 51 and gears 11, 12 and between the lower plate 52 and gears 11, 12.
  • the measurement of the axial distance s thus allows the selection of a Shim with the thickness s + 2x [ ⁇ m], where x represents a gap height between the gears 11, 12 and the top plate 51 and the lower plate 52.
  • the external gear pump 1 is designed as a compensated external gear pump 1.
  • the compensated variant of the external gear pump 1 has two Axialfeldplatten 54, 55 and two
  • the axial field seals 18, 19 have approximately the shape of a 3, as can already be seen in FIG.
  • the core of the external gear pump 1 is as follows: Due to the arrangement of the four sealing elements 61, 62, 63, 64 in the top plate 51 and in the lower plate 52, the working medium in the working space 6 is separated from any lubricant for lubricating the bearings 71, 72, 73, 74. Due to the separation of working medium and lubricant, the tribological conditions in the bearings 71, 72, 73, 74 are improved, which on the one hand reduces wear and on the other hand enables a reduction in the bearing diameter. This results in the same gear design to a greater distance between the root diameter of the gears 11, 12 and the inner diameters of the bearings 71, 72, 73, 74.
  • the lubricant of the bearings 71, 72, 73, 74 can also be used for cooling, so that overheating of the bearings 71, 72, 73, 74 is prevented.
  • the used plate design of the housing 2 allows a common part concept, which is a very cost-effective solution, especially with regard to various applications of the external gear pump 1.
  • the adaptation of all components of the plate construction according to their function - material adaptation is a very cost-effective solution, especially with regard to various applications of the external gear pump 1.
  • the illustrated external gear pump 1 is very well suited for low-lubricating, low-viscosity working media, as they are for example in
  • Waste heat recovery systems are used for internal combustion engines.
  • External gear pump 1 is therefore arranged in a waste heat recovery system of an internal combustion engine.
  • the internal combustion engine is supplied with oxygen via an air supply; after the combustion process
  • discharged exhaust gas is discharged through an exhaust pipe from the internal combustion engine.
  • the waste heat recovery system comprises a circuit carrying a working medium comprising, in the flow direction of the working medium, a feed fluid pump, an evaporator, an expansion machine and a condenser.
  • the working medium can be made as needed via a spur line from a
  • Sump and a valve unit are fed into the circuit.
  • the collecting container can alternatively be integrated into the circulation.
  • the evaporator is connected to the exhaust pipe of the internal combustion engine, thus uses the heat energy of the exhaust gas of the internal combustion engine.
  • Liquid working fluid is conveyed through the feed fluid pump, possibly from the reservoir into the evaporator and there through the
  • Working medium is then in the expansion machine under release of mechanical energy, for example, to a generator, not shown, or to a non-illustrated transmission relaxed. Subsequently, the working medium in the condenser is liquefied again and returned to the collecting container or fed to the feed fluid pump.
  • the feed fluid pump of the waste heat recovery system is an external gear pump 1 according to one of the above embodiments. These are particularly well suited for a waste heat recovery system, as they are also suitable for poorly lubricated working media with very low viscosities.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Abstract

L'invention concerne une pompe à engrenages extérieurs (1) comprenant un corps (2). Ce corps (2) comprend une plaque supérieure (51), une plaque inférieure (52) et une plaque de cadre (50). La plaque de cadre (50) est disposée entre la plaque supérieure (51) et la plaque inférieure (52). Un évidement formant une chambre de travail (6) est ménagé dans la plaque de cadre (50). Une première roue dentée (11) disposée sur un premier arbre (21) et une deuxième roue dentée (12) disposée sur un deuxième arbre (22) sont agencées dans la chambre de travail (6) de telle manière qu'elles engrènent l'une avec l'autre. Le premier arbre (21) et le deuxième arbre (22) font tous deux saillie à la fois à travers la plaque supérieure (51) et à travers la plaque inférieure (52). Un premier élément d'étanchéité (61) est disposé entre le premier arbre (21) et la plaque supérieure (51), un deuxième élément d'étanchéité (62) est disposé entre le premier arbre (21) et la plaque inférieure (52), un troisième élément d'étanchéité (63) est disposé entre le deuxième arbre (22) et la plaque supérieure (51) et un quatrième élément d'étanchéité (64) est disposé entre le deuxième arbre (22) et la plaque inférieure (52).
PCT/EP2017/083496 2016-12-21 2017-12-19 Pompe à engrenages extérieurs pour système de récuperation de chaleur perdue WO2018114919A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016225851.6 2016-12-21
DE102016225851.6A DE102016225851A1 (de) 2016-12-21 2016-12-21 Außenzahnradpumpe für ein Abwärmerückgewinnungssystem

Publications (1)

Publication Number Publication Date
WO2018114919A1 true WO2018114919A1 (fr) 2018-06-28

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ID=60813843

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2017/083496 WO2018114919A1 (fr) 2016-12-21 2017-12-19 Pompe à engrenages extérieurs pour système de récuperation de chaleur perdue

Country Status (2)

Country Link
DE (1) DE102016225851A1 (fr)
WO (1) WO2018114919A1 (fr)

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4130312C1 (fr) * 1991-09-12 1992-12-24 Hermann Berstorff Maschinenbau Gmbh, 3000 Hannover, De
EP1203885A2 (fr) * 2000-11-02 2002-05-08 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel Ltd.) Pompe à engrenages
DE102009045030A1 (de) 2009-09-25 2011-03-31 Robert Bosch Gmbh Zahnradpumpe mit Elektromotor
EP2587063A2 (fr) * 2011-10-31 2013-05-01 Nordson Corporation Pompe de mesure à engrenages avec un indicateur intégral
DE102013205648A1 (de) 2012-12-27 2014-07-03 Robert Bosch Gmbh System zur Energierückgewinnung aus einem Abwärmestrom einer Brennkraftmaschine
EP2837827A1 (fr) * 2013-06-27 2015-02-18 Sumitomo Precision Products Co., Ltd. Dispositif hydraulique
WO2016181520A1 (fr) * 2015-05-13 2016-11-17 株式会社 島津製作所 Pompe à engrenages

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19843161C2 (de) * 1998-09-21 2000-11-23 Hnp Mikrosysteme Gmbh Schichtstruktur-Gehäuseaufbau

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4130312C1 (fr) * 1991-09-12 1992-12-24 Hermann Berstorff Maschinenbau Gmbh, 3000 Hannover, De
EP1203885A2 (fr) * 2000-11-02 2002-05-08 Kabushiki Kaisha Kobe Seiko Sho (Kobe Steel Ltd.) Pompe à engrenages
DE102009045030A1 (de) 2009-09-25 2011-03-31 Robert Bosch Gmbh Zahnradpumpe mit Elektromotor
EP2587063A2 (fr) * 2011-10-31 2013-05-01 Nordson Corporation Pompe de mesure à engrenages avec un indicateur intégral
DE102013205648A1 (de) 2012-12-27 2014-07-03 Robert Bosch Gmbh System zur Energierückgewinnung aus einem Abwärmestrom einer Brennkraftmaschine
EP2837827A1 (fr) * 2013-06-27 2015-02-18 Sumitomo Precision Products Co., Ltd. Dispositif hydraulique
WO2016181520A1 (fr) * 2015-05-13 2016-11-17 株式会社 島津製作所 Pompe à engrenages

Also Published As

Publication number Publication date
DE102016225851A1 (de) 2018-06-21

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