WO2018224200A1 - Pompe à engrenages pour système de récupération de chaleur perdue - Google Patents

Pompe à engrenages pour système de récupération de chaleur perdue Download PDF

Info

Publication number
WO2018224200A1
WO2018224200A1 PCT/EP2018/058563 EP2018058563W WO2018224200A1 WO 2018224200 A1 WO2018224200 A1 WO 2018224200A1 EP 2018058563 W EP2018058563 W EP 2018058563W WO 2018224200 A1 WO2018224200 A1 WO 2018224200A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
pump
gear pump
cooling
shaft
Prior art date
Application number
PCT/EP2018/058563
Other languages
German (de)
English (en)
Inventor
Gerhard Lutz
Anselm Koch
Jakob Branczeisz
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 WO2018224200A1 publication Critical patent/WO2018224200A1/fr

Links

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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/0096—Heating; Cooling
    • 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
    • F04C2/10—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F04C2/102—Rotary-piston machines or pumps of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes
    • 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
    • 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
    • F04C2/123—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 radially or approximately radially from the rotor body extending tooth-like elements, co-operating with recesses in the other rotor, e.g. one tooth
    • 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
    • F04C2/126—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 radially from the rotor body extending elements, not necessarily co-operating with corresponding recesses in the other rotor, e.g. lobes, Roots 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
    • F04C2240/00—Components
    • F04C2240/60—Shafts
    • F04C2240/603—Shafts with internal channels for fluid distribution, e.g. hollow shaft

Definitions

  • the invention relates to a gear pump, preferably designed as an external gear pump, in particular a feed fluid pump, which is used in a waste heat recovery system of an internal combustion engine.
  • Feed fluid pumps are known in many ways from the prior art, for example as external gear pump from the post-published
  • an external gear pump which has at least two gears, which mesh with each other in the outer engagement and are rotatably supported by means of bearings. At least one of the bearings is designed as a magnetic bearing. The two gears are rotatably mounted about two mutually parallel axes of rotation in a housing of the external gear pump.
  • the invention relates to an optimized cooling of the gear pump, in particular a cooling of the bearings.
  • the gear pump according to the invention in particular embodied as Suitefluid- pump of a waste heat recovery system, has an optimized cooling by cool working fluid is passed through a cooling hole in a shaft of a gear and the flow is supported in the cooling hole by a feed wheel, so that the heat transfer coefficient of the Wave in the working medium rises.
  • the gear pump has a pump housing, in which an inlet, an outlet and a working space are formed.
  • a first gear and a second gear are arranged meshing with each other, wherein by means of the first gear and the second gear, a working fluid from the inlet to the outlet is conveyed.
  • the first gear is arranged on a shaft or formed integrally therewith.
  • a cooling hole is formed in the shaft.
  • the cooling bore is fluidly connected to the inlet.
  • a feed wheel for conveying the working medium is arranged.
  • the cooling bore can also completely penetrate the shaft so that the working medium can flow completely through it.
  • the cooling hole should be designed so that a high flow rate - and thus a high heat transfer coefficient - is realized on the largest possible area of the shaft.
  • the shaft is supported by means of a bearing arrangement, which is at least indirectly also cooled by the cooling of the shaft.
  • the rotating with the shaft conveyor wheel is a kind of flow pump, which the flow of the working medium used as the cooling medium through the cooling hole is amplified or even generated - this depends on the pressure conditions in the gear pump. As the flow rate increases, the heat transfer coefficient from the shaft into the cooling medium increases, so that the cooling effect increases.
  • the cooling hole is arranged upstream of the working space.
  • the cooling or working medium is used with a comparatively low temperature level, so that the cooling effect is increased.
  • the cooling bore forms the only fluidic connection between the inlet and the working space.
  • the entire - relatively cool - working fluid flows through the cooling hole, so that the flow rate - and with it the heat transfer coefficient - is relatively high. The cooling effect is thereby improved.
  • the cooling hole is arranged downstream of the inlet and upstream of the working space.
  • non-compressed and therefore not heated working fluid is passed through the cooling hole.
  • the effective temperature gradient between the working medium and the shaft is thus comparatively high, whereby the cooling effect is optimized.
  • the shaft is slidably mounted in the pump housing by means of a bearing arrangement.
  • the bearing assembly is arranged radially surrounding the shaft, so that a cooling of the shaft also leads to a cooling of the bearing assembly.
  • the bearing assembly may be for example a bearing bush or a bearing glasses.
  • the bearing assembly may also be a bearing pin formed on the pump housing, wherein the cooling bore is then guided on the bearing pin and at the same time at least partially constitutes a bearing surface.
  • the cooling capacity is maximized within the bearing assembly, so that very efficiently the heat loss or frictional heat from the vulnerable contact points - namely, in particular from the bearing assembly - is discharged. This is done by increasing the effective surfaces of the cooling hole with simultaneous active flow through this with relatively cool Ar- beitsmedium.
  • the already existing working medium is thus used advantageously; the flow of the working fluid through the cooling hole is amplified by the impeller.
  • an improvement in the temperature balance also has a positive effect on slide bearings with bearing materials with a higher load capacity, which permit permanent operation with mixed friction, if the viscosity of the working medium present in the contact points remains comparatively high due to the cooled comparatively low temperature.
  • the delivery wheel has a plurality of delivery blades-preferably four delivery blades. This represents a particularly effective embodiment for supporting or generating the flow of the working medium through the cooling hole.
  • the feed wheel has an inner ring with an additional bore formed therein.
  • a flow of the working medium is made possible by the additional bore. This is particularly advantageous in the loading and fulfillment of the gear pump, since this can be done without a rotation of the shaft or the bladed conveyor wheel.
  • the second gear is arranged on a further shaft or formed integrally therewith.
  • the further wave is one formed further cooling hole, wherein the further cooling bore is fluidly connected to the inlet.
  • a further delivery wheel for conveying the working medium is arranged in the further cooling bore.
  • the further shaft is therefore preferably cooled analogously to the shaft of the first gear.
  • the conveyor wheels used are identical.
  • the further cooling bore is arranged downstream of the inlet and upstream of the cooling bore.
  • the two cooling holes are connected in series, so that the working fluid can flow through them at maximum flow rate. Accordingly high are the two heat transfer coefficients in the two cooling holes.
  • the further cooling hole is arranged parallel to the cooling hole.
  • the cooling medium has a comparatively low temperature in both cooling bores.
  • the shaft - and optionally also the further shaft - made of a material with high thermal conductivity.
  • the material is a stainless steel.
  • At least one passage opening is formed in the shaft, via which the working medium can flow out of the cooling bore to the working space.
  • the cooling hole is not designed as a through hole, but as a blind hole, for example, in the event that the shaft represents the drive shaft of the gear pump.
  • the gear pump is designed as an external gear pump. These are very cost-effective in their production and have a robust operating behavior.
  • Gear pumps especially external gear pumps, are very suitable for use in waste heat recovery systems of internal combustion engines and when using low-viscosity working media. Therefore, the gear pump according to the invention is very advantageously usable in a waste heat recovery system.
  • the waste heat recovery system comprises a circuit carrying the working medium, wherein the circuit in the flow direction of the working medium comprises a feed fluid pump, an evaporator, an expansion machine and a condenser.
  • the feed fluid pump is designed as a gear pump with the features described above.
  • the gear pump is arranged downstream of the condenser and upstream of the evaporator, ie in the coldest region of the circuit; As a result, the cooling effect of flowing through the cooling medium working medium is maximized.
  • Fig. 2 is a section through an embodiment of an inventive
  • FIG. 3 is a sectional view of a similar embodiment of the gear pump of FIG. 2 with a sectional plane A-A,
  • Fig. 7 shows schematically a waste heat recovery system, wherein only the essential areas are shown.
  • the gear pump 1 shows a gear pump 1, designed as an external gear pump, from the prior art in an exploded view.
  • the gear pump 1 comprises a pump housing 2, a cover 3 and a bottom flange 4.
  • the lid 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 in this case have a certain number of teeth.
  • the first gear 1 1 is mounted on a shaft 21 and the second gear 12 on a parallel to the shaft 21 further shaft 22.
  • the 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 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 a respective press fit.
  • the shafts 21, 22 are mounted 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.
  • both bearing glasses 30, 40 are respectively two bushings 9 pressed.
  • the bearing bushes 9 of the bearing glasses 30 and 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 bearings for the two shafts 21, 22 from.
  • the two bearing bushes 9 can also be made in one piece with the bearing glasses 30. The same applies to the other bearing glasses 40th
  • the four bearing bushes 9 each have a radial bearing function and each form a sliding bearing with their associated shaft 21, 22.
  • the thrust bearing function is achieved by the two bearing glasses 30, 40:
  • the bearing glasses 30 frontally a stop surface 31 and the other bearing glasses 40 frontally a further 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.
  • seals on the pump housing 2 are arranged: a seal 28 between the pump housing 2 and the bottom flange 4, and a further seal 29 between the pump housing 2 and the lid 3. Both seals 28, 29 extend approximately annular over the circumference of the pump housing 2 and are usually arranged in corresponding grooves.
  • a Axialfelddichtung 18 is disposed between the bearing glasses 30 and the bottom flange 4, and between the other bearing glasses 40 and the cover 3, a further Axialfelddichtung 19 is arranged.
  • the two Axialfelddichtonne 18, 19 represent on the one hand an axial bearing of the two bearing glasses 30, 40 within the pump housing 2.
  • the front sides or rear sides of the two bearing glasses 30, 40 characterized angle of rotation either with the pressure level of the pressure range or with the pressure level the suction area acted upon.
  • the pump housing 2 of the gear pump 1 according to the invention comprises a front pump body 13 and a rear pump body 14.
  • housing seals 20 are arranged in the front pump body 13 and the rear pump body.
  • the first gear 11 and the second gear 12 meshing with each other in the working space 6 are arranged.
  • a stop plate 24 is arranged in the pump housing 2.
  • an axial field seal 10 is arranged directly on the run-on plate 24, which seals pressure-different areas on the back of the run-on plate 24 against each other.
  • the front pump body 13 has a recess 16 in which a shaft 21 or drive shaft 44 of the first gear 11 is received.
  • the first gear 11 is pressed onto the drive shaft 44 in the embodiment of FIG.
  • the drive shaft 44 and the first gear 11 are integrally formed.
  • a first bearing assembly 36 and a second bearing assembly 37 are further arranged.
  • the first bearing assembly 36 includes the first gear 11 and the drive shaft 44 and a first bearing pin 25.
  • the first gear 11 and / or the drive shaft 44 is radially mounted on the first bearing pin 25.
  • the second bearing arrangement 37 comprises the second gearwheel 12 and a second bearing journal 38.
  • the second gearwheel 12 is radially mounted on the second bearing journal 38.
  • the first journal 25 and the second journal 38 are formed as part of the pump housing 2.
  • a cooling passage 8 is formed, which is connected to an inlet 7 and an outlet 35 in the front pump body 13.
  • the cooling channel 8 is divided after the inlet 7 into a first partial cooling channel 80 and a second partial cooling channel 800, wherein the first partial cooling channel 80 extends through the first bearing arrangement 36 and the second partial cooling channel 800 through the second bearing arrangement 37 and this permeates.
  • These passage openings 17 connect the cooling channel 8 with a sub-channel 15 of the cooling channel 8, wherein the sub-channel 15 is connected to the working space 6 and formed in the front pump body 13.
  • the working medium flowing through the first partial cooling channel 80 and the second partial cooling channel 800 is recombined in the partial channel 15 of the cooling channel 8.
  • drainage channels 23 are formed, which connect the working space 6 via a lubrication gap 43 with the first partial cooling channel 80 and the second partial cooling channel 800, so that working fluid due to leakage from the working chamber 6 via a lubrication gap 43 in the first partial cooling channel 80 and / or the second partial cooling channel 800 can be passed and a Lager barnauerung takes place.
  • the lubricating gap 43 is formed between the first gear 11 and the first bearing pin 25 and the second gear 12 and the second bearing pin 38.
  • a delivery wheel 100 is arranged, wherein the cooling bore 45 is a region of the cooling channel 8.
  • the working medium with a low temperature level is sucked from the inlet 7 through the cooling channel 8 or the first partial cooling channel 80 and thus cools the first bearing arrangement 36 between the first gearwheel 11 or the drive shaft 44 and the first bearing journal 25.
  • the cooling takes place by forced Convection at the cooling hole 45 or on the wall of the first partial cooling channel 80th
  • FIG. 3 shows a section through the inventive gear pump 1 of Figure 2 with a sectional plane AA in a similar embodiment.
  • the recess 16 is shown for the drive shaft 44 of the first gear 11 in the pump housing 2, said recess 16 is fluidly connected to the sub-channel 15 of the cooling channel 8.
  • the sub-channel 15 of the cooling channel 8 extends in this embodiment around the recess 16.
  • the outlet 35 is separated by means of the axial field seal 10 of the sub-channel 15 of the cooling channel 8, so that no pressure level compensation between the outlet 35 and Partial channel 15 of the cooling channel 8 is made.
  • the axial field seal 10 is disposed in the front pump body 13 instead of, as shown in Figure 2, in the stop plates 24.
  • the stop plates 24 are less weakened.
  • volumetric losses caused by a closed shape of the axial field seal 10, as in FIG. 2 can be reduced by an open shape of the axial field seal 10, as in FIG.
  • the feed wheel 100 is arranged, for example, pressed.
  • the delivery wheel 100 has four blades 101, which serve to convey the working medium through the cooling channel 8 or through the first partial cooling channel 80.
  • the working medium also flows through the drive shaft 44 of the first gear 11 via the through-openings 17 and thus enters the working space 6 via a sub-channel 15.
  • the conveying wheel 100 rotating with the drive shaft 44 generates or supports the flow of the working medium through the cooling channel 8.
  • the working medium is conveyed by means of the first
  • FIG. 4 shows a further embodiment of the gear pump 1 according to the invention. Components of the same function are provided with the same reference numerals as in FIG. 4 shows the inventive gear pump 1 with the first bearing assembly 36 and the second bearing assembly 37.
  • the two shafts 21, 22 are in this embodiment in each case in one piece with the associated gear 11, 12 executed, but may alternatively be designed in two pieces.
  • the two first bearing bushes 39 and the two second bearing bushes 41 are inserted into the pump housing 2, for example, pressed.
  • the first gear 11 and the second gear 12 are radially mounted in the pump housing 2.
  • the first gear 11 and the second gear 12 are arranged meshing with each other in the working space 6.
  • the first bearing bushes 39 and the second bearing bushes 41 may be arranged in the pump housing 2 and form part of the pump housing 2.
  • the cooling channel 8 extends in this embodiment through the first gear 11 and the second gear 12, wherein the operation of the gear pump 1 is the same as in Fig.2.
  • the working medium enters the cooling channel 8 via the inlet 7 and thus flows through the first bearing arrangement 36 and the second bearing arrangement 37.
  • the first part cooling channel 80 of the cooling channel 8 is the cooling hole 45 in the first gear 11 and the second part cooling channel 800 of the cooling channel 8 as a further cooling bore 46 formed in the second gear 12.
  • the sub-channel 15 of the cooling channel 8 is connected in this embodiment as shown in Figure 2 with the working space 6 and performs the working fluid from the first part of the cooling channel 80 and the second partial cooling channel 800 together again.
  • the cooling channel 8 has a parallel connection of the first partial cooling channel 80 and the second partial cooling channel 800.
  • the entire working fluid is then rejoined in the sub-channel 15 and thus passes through the sub-channel 15 of the cooling channel 8 in the working space 6.
  • the first gear 11 and the second gear 12 convey the working fluid through the working space in the outlet 35th
  • first partial cooling channel 80 or in the cooling bore 45 and in the second partial cooling channel 800 or in the further cooling bore 46 is in each case a delivery wheel
  • the feed wheel 100, 110 arranged, which supports a flow through the partial cooling channels 80, 800 with working medium.
  • the feed wheel 100 is arranged in the cooling bore 45 of the drive shaft 44 and the first gear 11, for example, pressed into this.
  • Another feed wheel 110 is arranged in a further cooling bore 46 of the second gearwheel 12.
  • FIG. 5 shows a further embodiment of the gear pump according to the invention 1.
  • the first gear 11 and the second gear 12 are arranged meshing with each other.
  • the first gear 11 is disposed on the shaft 21 and the drive shaft 44, respectively. The executed as a drive shaft 44
  • Shaft 21 is sealed by means of a shaft seal 27 to the environment.
  • the second gear 12 is arranged on the further shaft 22.
  • the two shafts 21, 22 are rotatably supported by means of the two bearing glasses 30, 40 in the pump housing 2, as already described in Fig.l.
  • alternative embodiments with one-piece gear shafts 11, 12 and / or bearings by means of bushings 9 are possible.
  • first partial cooling channel 80 and the second partial cooling channel 800 are connected in series and connected by means of a connecting channel 88 formed in the bottom flange 4.
  • the first partial cooling channel 80 is in the
  • Cooling bore 45 of the shaft 21 is formed.
  • the second partial cooling channel 800 is formed in the further cooling bore 46 of the further shaft 22.
  • the second partial cooling channel 800 lies upstream of the first partial cooling channel 80.
  • three conveyor wheels 100, 110, 120 are arranged in the cooling channel 8:
  • the feed wheel 100 in the cooling bore 45 or in the first part of the cooling channel 80 at the opposite end to the through holes 17 of the cooling hole 45th The further delivery wheel 110 in the further cooling bore 46 or in the second partial cooling channel 800, adjacent to the inlet 7.
  • all three conveyor wheels 100, 110, 120 are pressed into the respective cooling bore 45, 46.
  • the working medium now passes through the following regions of the cooling channel 8, wherein the flow path is represented by the arrows:
  • the working medium enters the second partial cooling channel 800 via the inlet 7 formed in the cover 3 and flows through the further delivery wheel 110. It flows through at the end of the second Part cooling channel 800, the additional feed wheel 120 and flows through the connecting channel 88 to the first part of the cooling channel 80, where it flows through the feed wheel 100.
  • the working medium opens through the formed in the shaft 21 through holes 17 in the lid 3 formed in the sub-channel 15, from where it is the working space 6 is supplied.
  • the gear pump 1 as
  • the gears 11, 12 therefore promote a working medium along a housing inner wall of the pump housing 2.
  • the inventive gear pump 1 it is also possible to design the inventive gear pump 1 as an internal gear pump.
  • the cooling channel 8 preferably always forms the only hydraulic or fluidic connection between the inlet 7 and the working space 6.
  • the feeding of the uncompressed working medium from the inlet 7 into the cooling channel 8 is preferably designed such that no influences of the suction region of the gear pump 1 can have a disturbing effect.
  • additional processing of the lid 3 and / or the bottom flange 4 are carried out by the partial channel 15 and the connecting channel 88 are formed there.
  • the shafts 21, 22 are made hollow by the cooling bores 45, 46 and supplemented by a correspondingly integrated flow pump by the corresponding conveyor wheels 100, 110, 120. 6 shows an embodiment of a feed wheel 100, 110, 120 in a perspective view.
  • the feed wheel 100, 110, 120 has four feed vanes 101, 111,
  • the feed wheel 100, 110, 120 further comprises an outer outer ring 102, 112, 112,
  • the conveying blades 101, 111, 121 are arranged between the outer ring 102, 112, 122 and the inner ring 103, 113, 123.
  • an additional bore 104, 114, 124 is formed in the inner ring 103, 113, 123, through which working medium can also flow.
  • FIG. 7 shows a waste heat recovery system 200 of an internal combustion engine 210.
  • the internal combustion engine 210 is supplied with oxygen via an air supply 212; the exhaust gas discharged after the combustion process is discharged from the engine 210 through an exhaust pipe 211.
  • the waste heat recovery system 200 has a working medium leading circuit 200 a, which in the flow direction of the working medium a Feiseflu- idpumpe 202, an evaporator 203, an expansion machine 204 and a capacitor 205 includes.
  • the working medium can be fed as needed via a branch line from a sump 201 and a valve unit 201a in the circuit 200a.
  • the collecting container 201 may alternatively be incorporated into the circuit 200a.
  • the evaporator 203 is connected to the exhaust pipe 211 of the internal combustion engine 210, thus uses the heat energy of the exhaust gas of the internal combustion engine 210th
  • Liquid working fluid is conveyed through the feed fluid pump 202, possibly from the collecting container 201, into the evaporator 203 and evaporated there by the heat energy of the exhaust gas of the internal combustion engine 210.
  • the vaporized working medium is subsequently expanded in the expansion machine 204 with release of mechanical energy, for example to a generator, not shown, or to a transmission, not shown.
  • the working fluid in the condenser 205 is re-liquefied and returned to the sump 201 or fed to the feed fluid pump 202.
  • the above-described embodiments of the gear pump 1 are very well suited for use as a feed fluid pump 202 within the waste heat recovery system 100, since the working medium used there is low-viscosity and very aggressive and the functions of chemical resistance and cooling for the feed fluid pump 202 are very high important is. Overall, therefore, the life of the gear pump 1, 202 and the entire waste heat recovery system 200 is increased.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Details And Applications Of Rotary Liquid Pumps (AREA)
  • Rotary Pumps (AREA)

Abstract

La présente invention concerne une pompe à engrenages (1), notamment réalisée sous forme de pompe à fluide d'alimentation (102) d'un système de récupération de chaleur perdue (100), la pompe comprenant un carter (2) dans lequel sont formés une entrée (7), une sortie (35) et une chambre de travail (6). Une première roue dentée (11) et une deuxième roue dentée (12) sont disposées de manière à s'engrener l'une dans l'autre dans la chambre de travail (6), un fluide de travail pouvant être refoulé de l'entrée (7) à la sortie (35) dans la pompe à engrenages (1) au moyen de la première roue dentée (11) et de la deuxième roue dentée (12). La première roue dentée (11) est agencée sur un arbre (21, 44) ou est réalisée d'une seule pièce avec celle-ci. Un trou de refroidissement (45) est formé dans l'arbre (21, 44). Le trou de refroidissement (45) est en liaison fluidique avec l'entrée (7). Une roue de refoulement (100, 110, 120) destinée à refouler le fluide de travail est agencée dans le trou de refroidissement (45).
PCT/EP2018/058563 2017-06-07 2018-04-04 Pompe à engrenages pour système de récupération de chaleur perdue WO2018224200A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017209553.9 2017-06-07
DE102017209553.9A DE102017209553A1 (de) 2017-06-07 2017-06-07 Zahnradpumpe für ein Abwärmerückgewinnungssystem

Publications (1)

Publication Number Publication Date
WO2018224200A1 true WO2018224200A1 (fr) 2018-12-13

Family

ID=61911593

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2018/058563 WO2018224200A1 (fr) 2017-06-07 2018-04-04 Pompe à engrenages pour système de récupération de chaleur perdue

Country Status (2)

Country Link
DE (1) DE102017209553A1 (fr)
WO (1) WO2018224200A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113366220A (zh) * 2019-01-28 2021-09-07 费森尤斯医疗护理德国有限责任公司 齿轮泵

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4211516C1 (fr) * 1990-10-08 1993-07-22 Kabushiki Kaisha Kobe Seiko Sho, Kobe, Hyogo, Jp
DE69302291T2 (de) * 1992-02-03 1996-11-21 Smithske As Pumpe
JPH10131872A (ja) * 1996-10-28 1998-05-19 Shimadzu Corp ギヤポンプ
EP2940302A1 (fr) * 2012-12-28 2015-11-04 Daikin Industries, Ltd. Compresseur à spirale
DE102016214823A1 (de) 2016-08-10 2018-02-15 Robert Bosch Gmbh Außenzahnradmaschine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4211516C1 (fr) * 1990-10-08 1993-07-22 Kabushiki Kaisha Kobe Seiko Sho, Kobe, Hyogo, Jp
DE69302291T2 (de) * 1992-02-03 1996-11-21 Smithske As Pumpe
JPH10131872A (ja) * 1996-10-28 1998-05-19 Shimadzu Corp ギヤポンプ
EP2940302A1 (fr) * 2012-12-28 2015-11-04 Daikin Industries, Ltd. Compresseur à spirale
DE102016214823A1 (de) 2016-08-10 2018-02-15 Robert Bosch Gmbh Außenzahnradmaschine

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113366220A (zh) * 2019-01-28 2021-09-07 费森尤斯医疗护理德国有限责任公司 齿轮泵

Also Published As

Publication number Publication date
DE102017209553A1 (de) 2018-12-13

Similar Documents

Publication Publication Date Title
EP2921703B1 (fr) Unité pompes-moteur
EP3237728B1 (fr) Turbomachine
DE112013003114B4 (de) Turbinengenerator
DE102017106760A1 (de) Drehzahlerhöher
WO2018224200A1 (fr) Pompe à engrenages pour système de récupération de chaleur perdue
DE102009019418B4 (de) Umlaufverdrängerpumpe mit verbesserter Lagerschmierung
DE102015115841A1 (de) Pumpen-Motor-Einheit mit einer Kühlung eines die Pumpe antreibenden Elektromotors mittels Leckagefluid
DE102007035243A1 (de) Kopplungsanordnung
DE102017200485B3 (de) Hydraulikpumpe, insbesondere für ein Kraftfahrzeug
DE102014209624A1 (de) Turbomaschinen-Elektromaschinen-Einheit
WO2018114080A1 (fr) Pompe à engrenages pour système de récuperation de chaleur perdue
WO2018114921A1 (fr) Pompe à engrenages extérieurs pour un système de récupération de chaleur perdue
DE102010020299B4 (de) Pumpe mit Reibkupplungs-Drehzahlregelung
WO2018153605A1 (fr) Pompe à engrenage pour un système de récupération de chaleur
WO2018134019A1 (fr) Ensemble moteur-pompe conçu pour un système de récupération de chaleur
WO2018019587A1 (fr) Pompe à engrenages extérieurs pour un système de récuperation de chaleur perdue
DE102016216159A1 (de) Außenzahnradpumpe für ein Abwärmerückgewinnungssystem
WO2019072677A1 (fr) Pompe à engrenages extérieurs pour système de récupération de chaleur perdue
EP3536961B1 (fr) Pompe à vide à élément d'étanchéité
WO2018114919A1 (fr) Pompe à engrenages extérieurs pour système de récuperation de chaleur perdue
WO2018028916A1 (fr) Machine à roues dentées extérieures
WO2018114932A2 (fr) Pompe à engrenages extérieurs pour système de récuperation de chaleur perdue
WO2018114332A1 (fr) Pompe à fluide pour un système de récupération de chaleur perdue
WO2018114934A1 (fr) Pompe à engrenages extérieurs pour système de récuperation de chaleur perdue
DE3935116A1 (de) Verdraengerpumpe, insbesondere radialkolbenpumpe

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 18716218

Country of ref document: EP

Kind code of ref document: A1

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 18716218

Country of ref document: EP

Kind code of ref document: A1