WO2018114921A1 - Pompe à engrenages extérieurs pour un système de récupération de chaleur perdue - Google Patents

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

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Publication number
WO2018114921A1
WO2018114921A1 PCT/EP2017/083499 EP2017083499W WO2018114921A1 WO 2018114921 A1 WO2018114921 A1 WO 2018114921A1 EP 2017083499 W EP2017083499 W EP 2017083499W WO 2018114921 A1 WO2018114921 A1 WO 2018114921A1
Authority
WO
WIPO (PCT)
Prior art keywords
bearing
external gear
gear pump
housing
shaft
Prior art date
Application number
PCT/EP2017/083499
Other languages
German (de)
English (en)
Inventor
Eberhard Maier
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 WO2018114921A1 publication Critical patent/WO2018114921A1/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
    • 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

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 conveying pumps are widely known from the prior art, for example as external gear pumps from the published patent application DE 43 09 859 A1.
  • the external gear pump according to the invention has the advantage that it can be used for low-viscosity, poorly lubricating working media. Furthermore, the external gear pump is resistant to cavitation damage and can thus be used for operating temperatures close to the evaporation temperature of the working fluid to be pumped. Therefore, the external gear pump is particularly suitable for waste heat recovery systems of internal combustion engines, which often use low-viscosity working media.
  • the external gear pump has a housing.
  • the housing limits 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.
  • at least one slide bearing is arranged in each case in the housing.
  • the bearings are hydraulically connected by means of a connecting channel with the working space.
  • the connection channels are formed in the housing.
  • the formation of the connecting channels in the stationary housing and not in the rotating gear has a quasi static pressure of the working medium in the connecting channel and thus also in the respective downstream
  • Flushing the plain bearing has two main positive effects: on the one hand, the solid state friction is reduced by spraying working medium into the contact of the sliding bearing. On the other hand, a hot running of the plain bearing is prevented by a constant flow of working fluid is ensured. As a result, the temperature of the working medium does not increase in the contact of the sliding bearing, the viscosity therefore remains relatively high, so that the lubricating properties of the working medium - even in the case of a low-viscosity working fluid - are still comparatively good.
  • the housing comprises at least one bearing glasses.
  • the bearing glasses forms an axial bearing of the two gears.
  • bearing bushes can be arranged, for example pressed in, for the radial mounting of the two shafts in the bearing goggles.
  • the gears or the working space can be axially sealed, with an axial leakage is present, but can be minimized by an optimized gap height between bearing glasses and the end faces of the gears.
  • this requires the setting of a comparatively small gap height, which, moreover, may only be subject to slight tolerances, since otherwise, the structure of the hydrodynamic lubricating film of the low viscosity working fluid will not work.
  • the viscosity of the working medium is kept at a comparatively high level, so that consequently the gap height does not have to be tolerated too tightly.
  • two bearing bushes are arranged in the bearing goggles, each bearing bush forming a plain bearing for each shaft.
  • per bearing glasses per a radial bearing for both shafts are arranged in the bearing glasses. This optimizes the positioning of the two shafts, especially the parallelism. The efficiency of
  • connection channels are formed in the bearing goggles.
  • the connection channels can be made simple and inexpensive.
  • the connecting channels each comprise a groove on an end face of the bearing glasses.
  • the groove can simply be milled into the end face.
  • the connecting channels open - for example in the form of grooves - the working space side in a first tooth chamber of the first gear or the second gear.
  • the connection channels may also open into other tooth chambers, which have a pressure level higher than the pressure of the inlet.
  • pressurized working fluid is flushed into the associated slide bearing.
  • a corresponding pressure gradient ensures flushing of the sliding bearing. Otherwise, the working fluid would be in the plain bearing, the risk of hot running of the plain bearing would be given.
  • connection channels open into the associated lubrication gap of the plain bearing, viewed in the direction of rotation, on the bearing side immediately before the respective pressure field.
  • a lubricating wedge is formed directly in front of the pressure field, which is pressed into the contact of the sliding bearing, for example between the bearing bush and the shaft. The Solid state friction in the contact is minimized and thus also the wear in the plain bearing.
  • the connecting channels each comprise a cooling channel, which is arranged surrounding the respective sliding bearing outside.
  • the cooling channel the associated sliding bearing is arranged circumferentially by more than 180 °.
  • the respective sliding bearing is effectively cooled.
  • cooling the cavitation formation is reduced on the one hand and on the other hand increases the viscosity of the working medium and thus the lubricity. Both reduce wear in the plain bearings.
  • a large convection surface of the cooling channel coupled with a high flow is advantageous.
  • Waste heat recovery systems of internal combustion engines often use low viscosity, poorly lubricious working media.
  • the external gear pump according to the invention allows a good flushing and cooling of its plain bearings, so that wear and cavitation are reduced in the plain bearings. Therefore, the external gear pump according to the invention is very advantageous in one
  • Waste heat recovery system comprises a working medium leading circuit, 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 an external gear pump according to an embodiment with the features described above.
  • FIG. 1 shows an external gear pump of the prior art in
  • FIG. 2 is a schematic sectional view through an external gear pump of the prior art.
  • Fig. 3 is a schematic perspective view of an external gear pump according to the invention, wherein only the essential areas are shown.
  • Fig. 4 shows a section through an external gear pump according to the invention, wherein only the essential areas are shown.
  • 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 comprises a 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 housing 2 by four screws 5.
  • the housing 2, the cover 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. Alternatively, depending on a gear and a shaft also be made in one piece.
  • the first shaft 21 is used in the embodiment of Figure 1 as a drive shaft and is equipped with a not shown drive connected, 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
  • 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 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.
  • seal 28 between the housing 2 and the bottom flange 4, and a further seal 29 between the housing 2 and the lid 3.
  • Both seals 28, 29 extend approximately annular over the circumference of the housing 28, 29 and are usually arranged in corresponding grooves.
  • a first seal 28 between the bearing glasses 30 and the bottom flange 4 is a first
  • Axial field seal 18 arranged, 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 housing 2.
  • the end faces or rear sides of the two bearing glasses 30, 40 are characterized
  • External gear pump 1 in a schematic sectional view.
  • an inlet 2a and an outlet 2b are formed, which open on opposite sides in the working space 6.
  • a delivery volume V of the working medium is thus conveyed on the housing wall of the housing 2 between the teeth of the two gear wheels 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, atmospheric pressure - out, and in the region of the outlet 2b, the pressure range of the external gear pump 1 forms with a higher second
  • Pressure level - for example, 40 bar - off.
  • Pressure range depends on the following flow topology, for example, from a throttle point.
  • the second shaft 22 is formed in the embodiment of DE 43 09 859 A1 as a fixed bearing journal, so that the second gear 12 is mounted on the second shaft 22.
  • the lubricating gap 20 between the second gear 12 and the bearing pin 22 is supplied with working fluid.
  • 12 connecting channels 90 are formed in the second gear, from the tooth chambers - ie in the region of the tooth roots 12a - to the lubrication gap 20th
  • a connecting channel 90 is formed on each tooth root 12a, which is acted upon depending on the rotational angle of the second gear 12 with pressures between the pressure of the inlet 2a and the pressure of the outlet 2b.
  • Lubrication gap 20 is thus supplied over its entire circumference with working fluid, which is not required for optimal lubrication effect. This reduces the efficiency of known from the prior art
  • External gear pump 1 wherein only the essential areas are shown.
  • the external gear pump 1 is similar to that of Figure 1: for supporting the two shafts 21, 22 are on both sides of the gears 1 1, 12, the two bearing glasses 30, 40 are arranged, in which in turn two bearing bushes 9 are arranged.
  • Per bearing bushing 9, the external gear pump 1 has a connecting channel 90. In Figure 3, this is shown schematically only for a bearing bush 9; However, the external gear pump 1 preferably has a total of four connecting channels 90.
  • Connecting channel 90 however, not formed in a gear 1 1, 12, but in a stationary component, such as the bearing glasses 30 or the housing 2, depending on the design of the external gear pump. 1
  • Connecting channel 90 preferably branches off from a toothed chamber, which is acted upon by an average pressure, that is to say a pressure which does not correspond to the pressure of inlet 2a or the pressure of outlet 2b.
  • a feed point 90_b of the connecting channel 90 opens into the lubricating gap 20 between the bushing 9 and the shaft 21, 22, preferably in the direction of rotation immediately before the contact area between the shaft 21, 22 and bearing bushing.
  • FIG. 4 schematically shows a plan view of the bearing gland 30 with two bearing bushes 9 press-fitted therein.
  • a bearing bush 9 forms a sliding bearing 71 for the first shaft 21, and another bearing bush 9 forms a further sliding bearing 73 for the second shaft 22 the sliding bearing 71 and the first shaft 21 thus a lubricating gap 20_1 is formed, and between the other sliding bearing 73 and the second shaft 22, a further lubrication gap 20_3.
  • the lubrication gap 20_1 is communicated via the connection channel 90_1
  • connection channel 90_1 the effect of the associated connection channel 90_1 will be described below only with reference to the sliding bearing 71. Preferably, however, this should apply to all plain bearings of the two shafts 21, 22.
  • the direction of rotation R21 of the first shaft 21 is counterclockwise, so that the working fluid in the tooth chambers is conveyed from the inlet 2a to the outlet 2b. This results in the direction of the outlet 2b, a high
  • Fluid pressure and in the region of the inlet 2a a low fluid pressure.
  • a pressure field p21 is formed between the first shaft 21 and the sliding bearing 71.
  • the pressure field p21 is shown schematically and of several sizes such as the height of the
  • the extraction point 90_1_a is arranged in a region as sketched in FIG. 4, which is acted on by a pressure higher than the pressure of the inlet 2a, downstream of the connection channel 90_1
  • Gear 1 1 is optimal. Withdrawal point 90_1_a and Zuzhoustelle 90_1_b do not have to lie in the same plane to the axis of rotation R21, this is due in Figure 4 only the simplified representation.
  • connection channel 90_1 furthermore comprises a cooling channel 90_1_c between the removal point 90_1_a and the
  • Zu rawstelle 90_1_b in which the working fluid is flushed around the sliding bearing 71 to cool the sliding bearing 71.
  • the cooling channel 90_1_c can, as shown in FIG. 4, be formed in the bearing gland 30 or else in the bearing bushing 9.
  • the cooling channel 90_1_c runs around the sliding bearing by more than 180 ° in order to generate a comparatively large cooling surface.
  • the cooling of the sliding bearing 71 results in an increase in the viscosity of the working medium, so that the lubricating properties in the
  • Lubrication gap 20_1 be improved and consequently the wear in the sliding bearing 71 is reduced.
  • the external gear pump 1 has a housing 2, which comprises a bearing goggles 30, a further bearing gland 40 and an intermediate plate 50.
  • Intermediate plate 50 is disposed between the bearing glasses 30 and the other bearing glasses 40 and braced between them, for example screwed.
  • a recess is formed as a working space 6.
  • working space 6 arranged on the first shaft 21 first gear 11 and arranged on the second shaft 22 second gear 12 are arranged meshing with each other, as is the usual operating principle of
  • the four plain bearings 71, 72, 73, 74 preferably in the form of bearing bushes, arranged for the two shafts 21, 22:
  • a first sliding bearing 71 is disposed in the bearing bracket 30 for supporting the first shaft 21.
  • a second sliding bearing 72 is arranged in the further bearing glasses 40 for supporting the first shaft 21.
  • a third slide bearing 73 is disposed in the bearing bracket 30 for supporting the second shaft 22.
  • a fourth sliding bearing 74 is disposed in the further bearing goggles 40 for supporting the second shaft 22.
  • the three plain bearings 71, 73, 74 are in the embodiment of Figure 5 in
  • the second bearing 72 of the first shaft 21 designed as a drive shaft is quasi designed as a passage bearing, so that the first shaft 21 protrudes at this bearing 72 through the further bearing gland 40 or an additional component of the housing 2. Accordingly, a shaft sealing ring 65 is arranged between the other bearing glasses 40 and the additional component and the first shaft 21, which seals the working space 6 to the outside in the axial direction at the shaft drive.
  • the bearing glasses 30, the intermediate plate 50 and the other bearing glasses 40 are aligned by two dowel pins 59 and clamped together by screws, each having a sealing ring 82, 83 is disposed between the bearing glasses 30, 40 and the intermediate plate 50 to the housing 2 to the outside , in particular in the radial direction, seal.
  • the intermediate plate 50 forms the radial seal of the working space 6 and preferably contains the respective screwed connections to the
  • Intermediate 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, so that escapes from the tooth chambers only the smallest possible amount of leakage.
  • An axial sealing of the delivery chambers or tooth chambers between the teeth of the gears 11, 12 and the inner wall of the intermediate plate 50 and a minimization of the axial leakage is effected by the smallest possible
  • the two gap heights x on both ends of the gears 11, 12 are the same size.
  • the adjustment of the axial seal can preferably be made possible by a shim 53, which is arranged axially between the intermediate plate 50 and the other bearing glasses 40.
  • the external gear pump 1 has four connecting channels 90_1, 90_2, 90_3, 90_4, in each case one connecting channel for flushing through the four plain bearings 71, 72, 73, 74.
  • the four connecting channels 90_1, 90_2, 90_3, 90_4 are preferably hydraulically connected to a medium pressure of
  • the connecting channels 90_1, 90_2, 90_3, 90_4 are for this purpose formed in one or more components of the housing 2, for example in the bearing glasses 30 and the other bearing glasses 40th
  • connection channels 90_1, 90_2, 90_3, 90_4 each comprise a cooling channel, as shown in FIG.
  • 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.
  • the inventive concepts 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
  • Heat energy of the exhaust gas of the internal combustion engine evaporates.
  • the vaporized 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.
  • the connecting channels 90_1, 90_2, 90_3, 90_4 from the working space 6 to the four plain bearings 71, 72, 73, 74 the plain bearings 71, 72, 73, 74 are flushed with working fluid and cooled. It builds up in front of the pressure field of each one
  • the external gear pump 1 is also suitable for operating temperatures which are close to the evaporation temperature of the working medium, since the flushing of the plain bearings 71, 72, 73, 74 prevents a temperature increase to evaporation temperature and thus the risk of

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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

L'invention concerne une pompe à engrenages extérieurs dotée d'un carter. Le carter délimite une chambre de travail. Une première roue dentée disposée sur un premier arbre et une deuxième roue dentée disposée sur un deuxième arbre sont disposées dans la chambre de travail de manière à s'engrener l'une avec l'autre. Respectivement au moins un palier lisse est disposé dans le carter aux fins du montage radial des deux arbres. Les paliers lisses sont reliés de manière hydraulique à la chambre de travail au moyen respectivement d'un canal de liaison. Les canaux de liaison sont réalisés dans le carter.
PCT/EP2017/083499 2016-12-21 2017-12-19 Pompe à engrenages extérieurs pour un système de récupération de chaleur perdue WO2018114921A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016225859.1A DE102016225859A1 (de) 2016-12-21 2016-12-21 Außenzahnradpumpe für ein Abwärmerückgewinnungssystem
DE102016225859.1 2016-12-21

Publications (1)

Publication Number Publication Date
WO2018114921A1 true WO2018114921A1 (fr) 2018-06-28

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ID=60813845

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2017/083499 WO2018114921A1 (fr) 2016-12-21 2017-12-19 Pompe à engrenages extérieurs pour un système de récupération de chaleur perdue

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DE (1) DE102016225859A1 (fr)
WO (1) WO2018114921A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018008263A1 (de) * 2018-10-18 2020-04-23 Doris Korthaus Rotierende Verdrängerpumpe mit Gleitringdichtung

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2571377A (en) * 1947-05-15 1951-10-16 Prec Developments Co Ltd Rotary displacement pump
DE4309859A1 (de) 1993-03-26 1994-09-29 Bosch Gmbh Robert Zahnradmaschine
DE102013205648A1 (de) 2012-12-27 2014-07-03 Robert Bosch Gmbh System zur Energierückgewinnung aus einem Abwärmestrom einer Brennkraftmaschine
US20150354560A1 (en) * 2014-06-06 2015-12-10 Hamilton Sundstrand Corporation Gear pump drive gear pressure loaded bearing
WO2016052570A1 (fr) * 2014-09-30 2016-04-07 ダイキン工業株式会社 Pompe ou moteur à engrenages

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2891483A (en) * 1956-04-13 1959-06-23 Thompson Ramo Wooldridge Inc Movable bushing for pressure loaded gear pumps
US3528756A (en) * 1968-12-04 1970-09-15 Borg Warner Pressure loaded pump
JPH09317656A (ja) * 1996-05-31 1997-12-09 Shimadzu Corp ギヤポンプ

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2571377A (en) * 1947-05-15 1951-10-16 Prec Developments Co Ltd Rotary displacement pump
DE4309859A1 (de) 1993-03-26 1994-09-29 Bosch Gmbh Robert Zahnradmaschine
DE102013205648A1 (de) 2012-12-27 2014-07-03 Robert Bosch Gmbh System zur Energierückgewinnung aus einem Abwärmestrom einer Brennkraftmaschine
US20150354560A1 (en) * 2014-06-06 2015-12-10 Hamilton Sundstrand Corporation Gear pump drive gear pressure loaded bearing
WO2016052570A1 (fr) * 2014-09-30 2016-04-07 ダイキン工業株式会社 Pompe ou moteur à engrenages

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