WO2018114080A1 - Pompe à engrenages pour système de récuperation de chaleur perdue - Google Patents

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

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Publication number
WO2018114080A1
WO2018114080A1 PCT/EP2017/076414 EP2017076414W WO2018114080A1 WO 2018114080 A1 WO2018114080 A1 WO 2018114080A1 EP 2017076414 W EP2017076414 W EP 2017076414W WO 2018114080 A1 WO2018114080 A1 WO 2018114080A1
Authority
WO
WIPO (PCT)
Prior art keywords
gear
pump
bearing
gear pump
cooling channel
Prior art date
Application number
PCT/EP2017/076414
Other languages
German (de)
English (en)
Inventor
Guido Bredenfeld
Jakob Branczeisz
Matthias RIEDLE
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 WO2018114080A1 publication Critical patent/WO2018114080A1/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
    • 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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02—Arrangements of bearings
    • 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
    • F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
    • F04C15/06—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • 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
    • 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
    • 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 an external gear pump from the subsequently published DE 10 2016 214 823.
  • 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.
  • a storage cooling on the working medium is possible.
  • a cooling amount is diverted from the delivery rate of the working medium, which can then be flushed specifically in the direction of storage.
  • the gear pump according to the invention in particular embodied as a feed fluid pump of a waste heat recovery system, has the advantage that the entire working medium is used to cool the bearing of the gears so that no losses arise from the main flow of the working medium. As a result, the heat development at the bearing of the toothed wheels can be counteracted and a longer life of the entire
  • the gear pump in particular designed as a feed fluid pump of a waste heat recovery system, a pump housing, in which a
  • Inlet an outlet and a working space are formed.
  • a first gear and a second gear are meshingly arranged, wherein by means of the first gear and the second gear, a working fluid from the inlet to the outlet in the gear pump is conveyed.
  • the first In the pump housing, the first by means of a first bearing assembly
  • a cooling channel is formed for cooling the first bearing arrangement and the second bearing arrangement in the pump housing between the inlet and the working space, the cooling channel extending at least partially in the first bearing arrangement and in the second bearing arrangement.
  • the cooling channel can completely penetrate the first bearing arrangement and / or the second bearing arrangement, so that the working medium can flow completely through them.
  • the cooling channel can also be formed only partially in the first bearing arrangement and / or the second bearing arrangement, so that the cooling channel does not completely penetrate the bearing arrangements.
  • the cooling channel may be partially formed outside of the bearing assemblies.
  • the cooling channel may also comprise a plurality of sub-channels.
  • the heat balance of the bearings can be improved and, moreover, leads to an optimal heat balance and thus to an increased life of the entire gear pump.
  • a low temperature at the bearings results in a high viscosity of the working medium, so that a better lubrication of the working medium is produced.
  • known standard materials can be used to form the bearing arrangements, so that a cost saving is achieved, since it is not necessary to use particularly wear-resistant materials due to the better lubrication of the working medium.
  • the cooling channel forms the only hydraulic connection between the inlet and the working space.
  • the present invention uses the entire working fluid to cool the bearing assemblies.
  • the first bearing assembly comprises the first gear and a first journal.
  • the second bearing arrangement comprises the second gear and a second bearing journal.
  • the first bearing journal and / or the second bearing journal are advantageously designed as part of the pump housing.
  • the gear is radially supported by the first journal and the second gear through the second journal in the pump housing. The radial bearing of the first gear and the second gear possible misalignment within the pump housing and relative misalignment of the first gear and the second gear are prevented from each other and ensures full functionality of the gear pump.
  • the first bearing arrangement comprises the first gear and first bearing bushes.
  • the second bearing arrangement comprises the second gear and second bearing bushes.
  • the first bearing bushes and / or the second bearing bushes are preferably formed as part of the pump housing.
  • the embodiment of the bearing assembly with the bearing bushes leads to a radial bearing of the first gear and the second gear, so that misalignments in the pump housing or misalignments of the gears are prevented relative to each other and proper functioning of the gear pump is guaranteed.
  • the first bearing arrangement and the second bearing arrangement are preferably designed as plain bearings. In addition to cost-effective production and assembly, a small space is also necessary.
  • the first bearing assembly and the second bearing assembly is made of a material having high thermal conductivity, preferably aluminum, brass or steel, and for corrosion protection, a layer of a thermoplastic material, preferably PEEK or PAEK having ,
  • the bearing assembly may preferably comprise a layer of a thermoplastic such as PEEK (polyetheretherketone) or PAEK (polyaryletherketones).
  • the thickness of the Layer is preferably chosen so that it does not counteract the thermal conductivity of the material of the bearing assembly.
  • plastics such as preferably PEEK or PAEK, are very resistant to aggressive media and at the same time have very good tribological properties. Plastics do not corrode. The life of the gear pump is thereby increased. Especially in the application for working media of a waste heat recovery system, plastics are therefore very suitable.
  • At least one passage opening is formed in the first gearwheel and / or in the second gearwheel, via which working medium can enter the working space from the cooling passage via a subchannel of the cooling passage.
  • the pump housing includes a front pump body and a rear pump body. This allows easy manufacture and installation of the gear pump.
  • the pump housing stop plates are arranged, whereby the first gear and the second gear are mounted axially on the pump housing in the working space.
  • the starting plates for resistance to aggressive media from a thermoplastic material, such as PEEK, or graphite produced.
  • an axial field seal is arranged in the pump housing for pressure level regulation.
  • this is mounted between the front pump body and the rear pump body and connects directly to the stop plates. Different pressure areas on the back of the starting plates are sealed against each other.
  • the gears are for stabilizing and precisely aligning the gears within the gear pump and for full functionality of the gear pump via the pump housing, preferably the
  • a drain channel is formed, can be passed through which working fluid due to leakage from the working space via a lubrication gap in the cooling channel. This lubrication gap is created by the promotion of the working fluid through the gears through the working space.
  • Gear pump according to one of the preceding claims, characterized in that 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 the
  • 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 has a robust design, a cost-effective production and also a high wear protection.
  • 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. 4 is a sectional view of a similar embodiment of the gear pump of FIG. 2 with a sectional plane B-B,
  • FIG. 5 shows a section through a further embodiment of a gear pump according to the invention with a bearing arrangement of gears and bushings
  • Fig. 6 shows schematically a waste heat recovery system. Description of the embodiments
  • 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 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 a respective press fit.
  • the shafts 21, 22 are mounted on both sides of the gears 11, 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 11, 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 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 11, 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.
  • two 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 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.
  • stop plates 24 are formed in the pump housing.
  • an axial field seal 10 is arranged directly on the stop plates 24, which seals pressure-different areas on the back of the stop plates 24 against each other.
  • the front pump body 13 has a recess 16 in which a drive shaft 44 of the first gear 11 is received.
  • the drive shaft 44 in FIG. 2 includes the drive shaft 44 in FIG. 2 and is therefore designed in one piece with the latter. forms.
  • the drive shaft 44 and the first gear 11 are formed in two parts and are firmly connected to each other, for example by a press fit.
  • 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 a first bearing pin 25.
  • the first gear 11 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, the first partial cooling channel 80 passing through the first bearing arrangement 36 and the second partial cooling channel 800 passing through and penetrating the second bearing arrangement 37.
  • 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 barnauer 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.
  • 3 shows a section through the inventive gear pump 1 of Figure 2 with a sectional plane AA in a similar embodiment. In this case, components having the same function are provided with the same reference numerals as in FIG.
  • 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 partial channel 15 of the cooling channel extends around the recess 16 in this embodiment.
  • the outlet 35 is separated from the partial channel 15 of the cooling channel 8 by means of the axial field seal 10, so that no pressure level compensation between the outlet 35 and the partial channel 15 of the cooling channel 8 is produced.
  • 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. As a result, the stop plates 24 are less weakened.
  • volumetric losses caused by a closed form of the axial field gasket 10, as in FIG. 2 can be reduced by an open shape of the axial field gasket 10, as in FIG.
  • FIG. 4 shows a section through the inventive gear pump 1 of Figure 2 with a sectional plane B-B in a similar embodiment.
  • components having the same function are provided with the same reference numerals as in FIG. 4 shows a first cavity 32 for the first gear 11 with the drive shaft 44 and a second cavity 33 for the second gear 12.
  • the mounting of the first gear 11 on the first journal 25 and the bearing of the second gear 12 on the second journal 38 are also shown.
  • working fluid enters the cooling channel 8 through the inlet 7.
  • This is now divided into the first part of the cooling channel 80 and the second partial cooling channel 800, so that the working medium, the first bearing assembly 36 and the second bearing assembly 37 penetrates and the first gear 11 and the first bearing pin 25 and the second gear 12 and the second journal 38 flows through and flows around until it enters the working space 6.
  • 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 working medium is conveyed by means of the first gear 11 and the second gear 12 in the direction of the outlet 35.
  • 5 shows a further embodiment of the gear pump according to the invention 1. Parts of the same function are provided with the same reference numerals as in Figure 2.
  • 5 shows the gear pump 1 according to the invention with the first bearing arrangement 36 and the second bearing arrangement 37.
  • the first bearing arrangement 36 comprises the first gear 11 and first bearing bushes 39
  • the second bearing arrangement 37 comprising the second gear 12 and second bearing bushes 41
  • the first bearing bushes 39 and the second bearing bushes 41 are inserted into the pump housing 2.
  • 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 flows through and around the first bearing arrangement 36 and the second bearing arrangement 37.
  • 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 entire working medium thus also passes via the sub-channel 15 of the cooling channel 8 into 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
  • Sub-channel 15 of the cooling channel 8 and the outlet 35 has been drawn in a plane. It can be seen that, in particular, the partial channel 15 of the cooling channel 8, the working space 6 and the outlet 35 can not technically lie in one plane.
  • Figure 5 shows the embodiment of the gear pump 1 according to the invention therefore for illustrative purposes in a simplified schematic representation.
  • the cooling channel 8 is partially formed in the two bearing pins 25, 38, whereas in the embodiment in Figure 5, the cooling channel 8 is partially formed in the two gears 11, 12.
  • the cooling channel 8 is adjusted accordingly so that it runs in the bearing assemblies 36, 37.
  • the entire working medium is used in each embodiment, directly after the inlet 7 by means of a cooling channel 8, the bearing assemblies 36, 37 to flow or to flow through.
  • the cooling channel 8 may comprise a plurality of partial cooling channels 80, 800.
  • the working fluid is pre-cooled before entering the gear pump 1 and thus has the lowest temperature occurring for the medium at the inlet 7 of the gear pump 1.
  • the design of the cooling channel 8 can be made variable, as long as the cooling channel 8 extends at least partially in the bearing assemblies 36, 37 and the cooling channel 8 is also arranged between the inlet 7 and the working space 6 beyond. In this case, the cooling channel 8 forms the only hydraulic connection between the inlet 7 and the working space 6.
  • the gear pump 1 is designed as an external gear pump.
  • the gears 11, 12 therefore promote a working medium along a housing inner wall of the pump housing 2.
  • FIG. 6 shows a waste heat recovery system 100 of an internal combustion engine 110.
  • the internal combustion engine 110 is supplied with oxygen via an air supply 112; the exhaust gas discharged after the combustion process is discharged from the engine 110 through an exhaust pipe 111.
  • the waste heat recovery system 100 has a working medium leading circuit 100 a, which in the flow direction of the working medium idis pump 102, an evaporator 103, an expansion machine 104 and a condenser 105 includes.
  • the working medium can be fed as needed via a branch line from a sump 101 and a valve unit 101a in the circuit 100a.
  • the collecting container 101 may alternatively be incorporated into the circuit 100a.
  • the evaporator 103 is connected to the exhaust pipe 111 of the internal combustion engine 110, thus uses the heat energy of the exhaust gas of the internal combustion engine 110th
  • Liquid working medium is conveyed by the feed fluid pump 102, possibly from the collecting container 101, into the evaporator 103 and vaporized there by the heat energy of the exhaust gas of the internal combustion engine 110.
  • the vaporized working medium is subsequently expanded in the expansion machine 104 with release of mechanical energy, for example to a generator, not shown, or to a transmission, not shown.
  • the working medium in the condenser 105 is liquefied again and returned to the collecting container 101 or fed to the feed fluid pump 102.
  • the above-described embodiments of the gear pump 1 are very well suited for use as a feed fluid pump 102 within the waste heat recovery system 100, since the working medium used there is low-viscosity, very aggressive, and the chemical-resistance function of the feed fluid pump 102 is very important. Overall, therefore, the life of the gear pump 1, 102 and the entire waste heat recovery system 100 is increased.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Details And Applications Of Rotary Liquid 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), comprenant un carter de pompe (2) dans lequel sont réalisés une entrée (7), une sortie (35) et un espace de travail (6). En l'occurrence, une première roue dentée (11) et une deuxième roue dentée (12) sont disposées de manière à s'engrener l'une dans l'autre dans l'espace de travail (6), un fluide de travail pouvant être refoulé depuis l'entrée (7) jusqu'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 supportée au moyen d'un premier agencement de palier (36) et la deuxième roue dentée (12) est supportée au moyen d'un deuxième agencement de palier (37) dans le carter de pompe (2). En outre, pour le refroidissement du premier agencement de palier (36) et du deuxième agencement de palier (37), un canal de refroidissement (8) est réalisé dans le carter de pompe (2) entre l'entrée (7) et l'espace de travail (6), le canal de refroidissement (8) s'étendant au moins en partie dans le premier agencement de palier (36) et dans le deuxième agencement de palier (37).
PCT/EP2017/076414 2016-12-21 2017-10-17 Pompe à engrenages pour système de récuperation de chaleur perdue WO2018114080A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016225883.4A DE102016225883A1 (de) 2016-12-21 2016-12-21 Zahnradpumpe für ein Abwärmerückgewinnungssystem
DE102016225883.4 2016-12-21

Publications (1)

Publication Number Publication Date
WO2018114080A1 true WO2018114080A1 (fr) 2018-06-28

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PCT/EP2017/076414 WO2018114080A1 (fr) 2016-12-21 2017-10-17 Pompe à engrenages pour système de récuperation de chaleur perdue

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WO (1) WO2018114080A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE102017218882B3 (de) 2017-10-23 2019-01-24 Technische Universität Dresden Außenverzahnte Zahnradpumpe und Drehantrieb mit einer Zahnradpumpe

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JP2013053534A (ja) * 2011-09-01 2013-03-21 Seiko Epson Corp ポンプ、及び、流体噴射装置

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