WO2008138712A1 - Unité de pompage pourvue d'une pompe principale et d'une pompe auxiliaire - Google Patents

Unité de pompage pourvue d'une pompe principale et d'une pompe auxiliaire Download PDF

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Publication number
WO2008138712A1
WO2008138712A1 PCT/EP2008/054865 EP2008054865W WO2008138712A1 WO 2008138712 A1 WO2008138712 A1 WO 2008138712A1 EP 2008054865 W EP2008054865 W EP 2008054865W WO 2008138712 A1 WO2008138712 A1 WO 2008138712A1
Authority
WO
WIPO (PCT)
Prior art keywords
pump
pair
drive shaft
control
auxiliary pump
Prior art date
Application number
PCT/EP2008/054865
Other languages
German (de)
English (en)
Inventor
René Constantin SCHEERER
Stefan Merz
Martin Josef Zug
Gordon Ulrich Mohn
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 WO2008138712A1 publication Critical patent/WO2008138712A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/10—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type
    • F04B23/106—Combinations of two or more pumps the pumps being of different types at least one pump being of the reciprocating positive-displacement type being an axial piston pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B23/00—Pumping installations or systems
    • F04B23/04—Combinations of two or more pumps
    • F04B23/08—Combinations of two or more pumps the pumps being of different types
    • F04B23/12—Combinations of two or more pumps the pumps being of different types at least one pump being of the rotary-piston positive-displacement type

Definitions

  • the invention relates to a pump unit having a main pump and an auxiliary pump, which is arranged in a housing part of a housing of the pump unit, and which are driven by a common drive shaft, wherein the main pump has a first pair of control openings with a first center axis and the auxiliary pump, a second pair of control openings having a second central axis.
  • a pump unit with a main pump and an auxiliary pump is known.
  • the main pump which is designed as an axial piston machine, and the auxiliary pump are driven by a common drive shaft.
  • the auxiliary pump is arranged in a connection plate of the axial piston machine.
  • the auxiliary pump is designed as a drive slide pump, wherein the rotor of the drive slide pump is arranged on a bearing in the connection plate penetrating shaft end of the common drive shaft.
  • a bearing for rotatably supporting the common drive shaft is inserted into the connection plate on the side facing the inside of the housing.
  • connection plate is so long in the axial direction that the plane in which the connections of the main pump are made, and the plane in which the connections of the auxiliary pump are arranged, in the axial direction spaced from each other.
  • the arrangement of the inlet and outlet lines for both the auxiliary pump and for the main pump therefore do not influence each other regardless of their location in the terminal plate.
  • the full cross-section of the connection plate for the cable routing is available in each case.
  • such an arrangement leads to a considerable length of the connection plate and thus to a considerable length of the entire pump unit.
  • the distance of the auxiliary pump is increased by the bearing of the drive shaft. Due to the floating mounting of the rotor of the auxiliary pump on the free shaft end, the deflection of the shaft increases.
  • Drive shaft are arranged offset. This not only increases the length, but the shaft penetrating the bearing stub shaft of the common drive shaft reaches a considerable length. This favors the deflection of the shaft.
  • the pump unit according to the invention has a main pump and an auxiliary pump.
  • the auxiliary pump is arranged in a housing part of a housing of the pump unit.
  • the auxiliary pump and the main pump are driven by a common drive shaft, to which the auxiliary pump and the main pump are connected to this common drive shaft.
  • the main pump is connected via a first pair of control ports with a first central axis with a hydraulic circuit.
  • the auxiliary pump is connected via a second pair of control openings with a second central axis with the hydraulic circuit.
  • the term "central axis" of the control openings is subsequently also used in non-symmetrical control openings.
  • the "center axes" are defined by an imaginary line which defines the suction side from the delivery side of the main pump (first central axis) and the suction side from the delivery side of the auxiliary pump (second central axis).
  • a non-symmetrical arrangement or shaping of the control openings can be used, for example, to achieve a pre-compression.
  • the first pair of control openings and the second pair of control openings are arranged in a housing part such that the second center axis of the second pair of control openings with a plane defined by the first center axis of the first pair of control openings and a rotation axis of the common drive shaft encloses a 90 degree shifting angle ,
  • the first pair of control openings and the second pair of control openings are twisted relative to one another in the housing part.
  • the lines through which the main pump and the auxiliary pump are connected to the hydraulic circuit can thus be guided in each case in an area of the housing part that leading to the first pair of control ports connecting lines and leading to the second pair of control ports connecting lines not in a spatial conflict with each other.
  • the second central axis it is advantageous for the second central axis to intersect the plane defined by the axis of rotation of the common drive shaft and the first central axis at an angle which is also different from zero degrees.
  • the connecting lines for the main pump are led from the control openings in the radial direction to the outside.
  • the connecting lines of the main pump thus run substantially in a direction which is between zero degrees and 90 degrees to the first center axis of the first pair of control openings.
  • the rotation of the second pair of control apertures relative to the first pair of control apertures is such that the second central axis of the second pair of control apertures communicate with the level one zero degrees and
  • 90 degrees includes different angles, thereby making it possible to provide not only the connection lines for the second pair of control openings in the Um Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff Kunststoff, a cam ring in the case of the adjustable auxiliary pump.
  • Such an adjustment means and / or a return device which counteracts the adjustment means and is arranged opposite the adjustment means, preferably extends substantially along the second center axis of the second pair of control openings.
  • the angle between the plane defined by the first center axis of the first pair of control ports and the axis of rotation of the common drive shaft and the second center axis of the second pair of control ports is an angle OC which is from at least 35 degrees to 55 degrees inclusive.
  • Such an angle between the first center axis and the second center axis and thus ultimately between the first pair of control openings and the second pair of control openings allows a particularly efficient utilization of the installation space of the connection plate.
  • the auxiliary pump has a rotor and this rotor is arranged by means of a torque-transmitting driving device on the free shaft end of the drive shaft.
  • the free end of the shaft have a driving toothing, which corresponds to a driving bearing of the rotor, wherein the
  • a vane pump or a roller-cell pump is particularly preferably used.
  • vane pumps or roller cell pumps can be advantageously used the available space with a reliable pump technology.
  • Fig. 1 shows a longitudinal section through a pump unit according to the invention with a cantilevered
  • FIG. 2 shows a first illustration of a connection plate of the pump unit according to the invention from the side facing the main pump;
  • FIG. 3 shows a second view of the connection plate of the pump unit according to the invention from the side receiving the auxiliary pump;
  • Fig. 4 is a schematic representation of the free
  • Figure 5 is a schematic representation for explaining the problem in the deflection of the drive shaft in a flying storage.
  • Fig. 6 is a schematic representation to illustrate the operation of the spherical design of a
  • a preferred embodiment of a pump unit 1 is shown, the a housing having a cup-shaped housing part 2 and a cup-shaped housing part 2 closing further housing part.
  • the further housing part is designed as a connection plate 3.
  • a main pump 4 is arranged in the interior of the cup-shaped housing part 2.
  • An auxiliary pump 5 is arranged in a side facing away from the cup-shaped housing part 2 side of the connection plate 3.
  • the auxiliary pump 5 may be provided in a two-stage pump unit 1 as a charge pump of the main pump 4.
  • the auxiliary pump 5 is provided as a feed pump for a operated by the pump unit 1 hydraulic system.
  • the main pump 4, which is designed as an axial piston machine in the illustrated embodiment, and the auxiliary pump 5 are driven by a common drive shaft 6.
  • the drive shaft 6 has a guided out of the cup-shaped housing part 2 in the region of the bottom shaft end.
  • a toothing 7 is formed at the shaft end of the drive shaft 6, .
  • the toothing 7 serves a rotationally fixed connection of the drive shaft 6 with a torque generating device.
  • the common drive shaft 6 is rotatably supported by means of a first bearing 8 and a second bearing 9 in the housing of the pump unit 1 and thus rotatable about an axis of rotation.
  • the first bearing 8 is arranged in the bottom of the cup-shaped housing part 2.
  • bearing 9 is arranged in the connection plate 3 on the side of the connection plate 3 facing the interior of the cup-shaped housing part 2.
  • a cylinder drum 10 is rotatably connected.
  • a plurality of cylinder bores are formed.
  • the cylinder bores are arranged distributed on a circumferential circle and extend parallel to the axis of rotation.
  • a piston 11 is arranged longitudinally displaceable.
  • a sliding shoe 12 is pivotally connected, via which the piston 11 is supported on a swash plate 13.
  • Swash plate 13 has a tread on which the sliding blocks 12 at a rotation of the
  • the cylinder bores are open.
  • the cylinder bores communicate via openings formed in a control plate 14 alternately with a first control port 15 or a second control port 16 of the port plate 3.
  • the first control port 15 and the second control port 16 are kidney shaped, as described below with reference to FIG Figs. 2 and 3 will be explained.
  • the first and the second control openings 15, 16 together form a first pair of control openings 15, 16.
  • the first control opening 15 is connected to an inlet line 17 and the second control opening 16 is connected to an outlet line 18. Via the first control opening 15, pressure fluid from the inlet line 17 is drawn in at a stroke movement of the piston 11 which enlarges the volume in the cylinder bore.
  • control plate 14 preferably has passage openings, which correspond in terms of their geometry with the geometry of the first and the second control opening 15, 16.
  • a dowel pin can be provided.
  • the cylinder drum 10 is acted upon by means of a spring force in the direction of the control plate 14, so that a sealing contact of the side facing away from the swash plate 13 end face of the cylinder drum 10 is ensured on the control plate 14.
  • the common drive shaft 6 has a free shaft end 19.
  • the free shaft end 19 penetrates the second bearing 9 and protrudes into a stepped recess 24 of the connection plate 3.
  • the stepped recess 24 of the connection plate 3 receives on its side facing away from the interior of the housing side, the components of the auxiliary pump 5.
  • the auxiliary pump 5 is designed as a vane pump.
  • the rotor 20 is disposed on the free shaft end 19 of the common drive shaft 6 by means of a torque transmitting device.
  • a torque-transmitting device may be a splined connection or a splined connection.
  • a driving toothing is formed on the free shaft end 19, which engages in a corresponding driving bearing on the part of the rotor 20.
  • the auxiliary pump 5 is designed as a vane pump.
  • a plurality of grooves in the radial direction or approximately radial direction are introduced in the rotor 20.
  • one of the grooves 21 is visible.
  • a movable element 22 is arranged in the grooves.
  • the movable, radially displaceable element 22 is moved in the radial direction outwards due to the centrifugal force, so that it sealingly against a inner circumferential surface of a cam ring 23 abuts.
  • an unillustrated guide ring can be provided.
  • the displaceable element 22 can be acted upon hydraulically with a radially outward acting force.
  • the cam ring 23 is in terms of its relative position with respect to the axis of rotation of the common
  • the pressure prevailing in the inlet line 17 is supplied to the cam ring 23 for generating a control force.
  • the inlet line 17 is connected via an actuating pressure channel 26 to a sickle-shaped gap forming a pressure chamber.
  • the gap is formed between the cam ring 23 and the recess 24 on the side directed towards the outside
  • the recess 24 in addition to the cam ring 23 and the rotor 20 is inserted.
  • the recess 24 is closed by a cover 25.
  • the lid 25 is sealed, for example via an O-ring seal and bolted to the connection plate 3.
  • FIG. 2 shows a view of the connection plate 3 from the side of the main pump 4 in the direction of the axis of rotation. It can be seen that the first control opening 15 and the second control opening 16 are kidney-shaped and extend along a respective section of a circular arc.
  • the first control port 15 is connected to the inlet duct 17, while the second control port 16 is connected to the outlet duct 18 of the main pump 4.
  • the inlet pipe 17 and the outlet pipe 18 extend in opposite directions from the control openings 15, 16.
  • the first control opening 15 and the second control opening 16 are arranged symmetrically to a first central axis 31.
  • the inlet conduit 17 and the outlet conduit 18 extend along a line 32 which is perpendicular to the first central axis 31 of the first pair of control openings 15, 16.
  • a second pair of control openings 27 and 28 is provided for supplying and discharging pressure medium to and from the auxiliary pump 5.
  • the second pair of control openings 27 and 28, which consists of the third control opening 27 and the fourth control opening 28, is shown in dashed lines in FIG. This indicates that in the view shown in FIG. 2, the second pair of control openings 27, 28 is actually hidden.
  • the first pair of control openings 15, 16 and the second pair of control openings 27, 28 are arranged twisted to each other.
  • the control openings of the second pair of control openings 27, 28 are in turn kidney-shaped and are symmetrical with respect to a second central axis 37.
  • the rotation of the first central axis 31 to the second central axis 37 is described by an intermediate angle CC, the second Central axis 37 with the first central axis 31 in the vertical projection of Fig. 2 includes.
  • this angle OC is in any case not equal to 90 degrees and preferably also not equal to zero degrees. In particular, it is preferred if the angle OC is at least 35 degrees, but at most 55 degrees, as shown in the example shown. In this orientation of the second central axis 37 with respect to the first central axis 31, it is possible to carry out the auxiliary pump 5 as an adjustable pump without the length of the
  • the third control port 27 forms a suction-side control kidney of the auxiliary pump 5.
  • the third control port 27 is connected to a suction channel 29.
  • the suction channel 29 is formed in a connection bend 30, which is provided laterally on the connection plate 3.
  • Pressure medium is connected to the fourth control port 28, an outlet passage 33.
  • the exhaust passage 33 annularly at least partially surrounds the intake passage 17.
  • auxiliary pump 5 is designed as an adjustable pump, as has already been explained in FIG. 1, a restoring force must be provided against the control pressure taken from the inlet line 17 and the auxiliary pump 5 can be switched off as the control pressure decreases
  • a bore 34 is provided along the second central axis 37, which receives a corresponding return device.
  • the relative position of the control ports of the first pair of control ports 15, 16 and the second pair are not shown and will be explained below with reference to FIG. 3.
  • the return device may be disposed in the bore 34 without requiring a change in the routing of the inlet line 17 and the outlet line 18.
  • a differently designed adjusting means may be provided at the diametrically opposite end of the central axis 37 and there generate a force on the cam ring 23.
  • FIG. 3 shows a further view of the connection plate 3 from the side facing away from the main pump 4.
  • a return device 36 is arranged in the bore 4.
  • Return device 36 includes a plug 35 which is secured in the bore 4 via a screw connection.
  • the plug 35 simultaneously forms a first spring bearing for a return spring 42.
  • the plug 35 is hollow drilled on its side facing the cam ring. This leads to a reduction in space, since the return spring 42 can engage in the hollow-drilled area.
  • a disc or a ring is provided to support the return spring 42 in the hollowed plug 35 .
  • the return spring 42 is designed as a spiral spring and exercises with screwed Plug 35 a force in the direction of the second center axis 37 on the in Fig. 3 for clarity not shown cam ring 23 from. By this spring force of the cam ring 23 is acted upon by a force acting in the direction of increasing delivery volume of the auxiliary pump 5 force. In the opposite direction acts on the formed between the recess 24 and the cam ring 23 a control pressure.
  • Fig. 3 also shows a first stop 38 and a second stop 39.
  • the two stops 38, 39 are preferably in the circumferential direction on both sides of
  • the auxiliary pump 5 when still cold pressure medium due to the high viscosity of the pressure medium, the auxiliary pump 5 is brought into its control range. It occurs at high viscosities, as they occur in cold pressure media, high traffic jams on.
  • the cam ring 23 is held by the stops 38 and 39 in a position so that the delivery rate of the auxiliary pump 5 is sufficient to supply in the case of execution of the auxiliary pump 5 as a charge pump, the main pump 4 with pressure medium.
  • the stops 38 and 39 can also be omitted.
  • an adjustable stop can be provided instead of the fixed stops 38 and 39. This is realized for example by a threaded pin which is screwed into the plug 35.
  • the deflection of the drive shaft 6 has a negative effect on the running behavior and in particular on the wear resistance of the auxiliary pump 5.
  • a slightly convex driving teeth 40 is formed, which is shown in simplified form in FIG.
  • the driving toothing 40 is designed with a radius 41, which can be seen in the partially cut free shaft end 19 of FIG.
  • the driving teeth 40 with a radius 41, it is possible to slightly incline the axis of rotation of the drive shaft 6 in the region of the free shaft end 19 with respect to the positional plane of the rotor 20, so that the positional plane of the rotor 20 and the axis of rotation of the drive shaft 6 in the area of the free shaft end 19 include an angle different from 90 °.
  • the crowned driving toothing 40 at the free end 19 of the drive shaft 6 can also be the corresponding
  • Mit Erasmuslagerung which is formed in the interior of the rotor 20, be provided with a curved geometry. Since the embodiment with a crowned entrainment toothing 40 at the free end 19 of the drive shaft 6 is easier to realize in terms of manufacturing technology, it is preferred.
  • FIG. 5a shows a cylindrical entrainment device of a shaft end 19 'of a drive shaft and of a rotor 20' arranged thereon. If, due to transverse forces, the free shaft end 19 'of the drive shaft now deflects, as shown schematically in FIG. 5b, the rotor 20 is tilted and rests against the connection plate 3 on the one hand and against the cover 25 on the other.
  • Connection plate 3 and the cover 25 does not change anything, it can be seen in Fig. 6b that the parallel orientation of the position or rotation plane of the rotor 20 to the terminal plate 3 and the lid 25 also in a
  • the drive shaft 6 penetrates the rotor 20 and is mounted again on the side facing away from the main pump 4 side of the rotor 20 in order to absorb the transverse forces occurring and to reduce the associated deflection of the drive shaft 6.
  • the inventive Arrangement of the first pair of control openings 15, 16 and the second pair of control openings 27, 28 relative to each other is also advantageous in multi-part drive shafts. In this case, a first drive shaft part of the main pump 4 via a clutch hub with a second
  • the second drive shaft part of the auxiliary pump 5 is connected.
  • the second drive shaft part drives the rotor 20 and can also be mounted on both sides of the rotor 20. Even with such an arrangement, the rotation of the control openings 15, 16 and 27, 28 according to the invention leads to the desired
  • connection plate 3 is slimmer in the outer region, since an extension of the connection plate 3 is required only for receiving the bearing near the center.
  • auxiliary pump 5 may also be designed as a roller-cell pump instead of the vane-cell pump specified in the example.

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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

Unité de pompage pourvue d'une pompe principale et d'une pompe auxiliaire qui est située dans une partie (3) du corps de l'unité de pompage. La pompe auxiliaire et la pompe principale sont entraînées par un arbre d'entraînement commun. La pompe principale comporte une première paire d'ouvertures de commande (15, 16) présentant un premier axe médian (31) et la pompe auxiliaire comporte une seconde paire d'ouvertures de commande (27, 28) présentant un second axe médian (37). La première paire d'ouvertures de commande (15, 16) et la seconde paire d'ouvertures de commande (27, 28) sont placées dans la partie (3) du corps de l'unité de pompage de manière telle que le second axe médian (37) forme avec un plan défini par le premier axe médian et par un axe de rotation de l'arbre d'entraînement commun (6) et du premier axe médian (31) un angle (OC) différent de 90 degrés.
PCT/EP2008/054865 2007-05-16 2008-04-22 Unité de pompage pourvue d'une pompe principale et d'une pompe auxiliaire WO2008138712A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102007022969.2 2007-05-16
DE102007022969 2007-05-16
DE102007032102.5 2007-07-10
DE102007032102A DE102007032102A1 (de) 2007-05-16 2007-07-10 Pumpeneinheit mit Hauptpumpe und Hilfspumpe

Publications (1)

Publication Number Publication Date
WO2008138712A1 true WO2008138712A1 (fr) 2008-11-20

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ID=39868907

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Application Number Title Priority Date Filing Date
PCT/EP2008/054865 WO2008138712A1 (fr) 2007-05-16 2008-04-22 Unité de pompage pourvue d'une pompe principale et d'une pompe auxiliaire

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DE (1) DE102007032102A1 (fr)
WO (1) WO2008138712A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105484967A (zh) * 2014-10-07 2016-04-13 罗伯特·博世有限公司 带有主泵和辅助泵的泵装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102011117687B4 (de) 2011-11-04 2022-05-19 Robert Bosch Gmbh Hydraulisches System mit einer Hauptpumpe und mit einer Speisepumpe
DE102012207137B4 (de) * 2012-04-27 2014-10-09 Zf Friedrichshafen Ag Bauteillagerung

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US2604047A (en) * 1945-09-19 1952-07-22 Hulman Two-stage hydraulic pressure pump
DE10117373A1 (de) * 2001-04-06 2002-10-10 Mannesmann Rexroth Ag Hydraulisches Pumpenaggregat
DE102004009838A1 (de) * 2004-02-28 2005-09-22 Zf Lenksysteme Gmbh Flügelzellenpumpe
US7007468B1 (en) * 2003-06-27 2006-03-07 Hydro-Gear Limited Partnership Charge pump for a hydrostatic transmission

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US2870746A (en) 1954-11-19 1959-01-27 Vickers Inc Servo control for power transmission
DE2236751A1 (de) 1972-07-26 1974-02-07 Linde Ag Axialkolbenmaschine
DE3301563A1 (de) * 1983-01-19 1984-07-26 Zahnradfabrik Friedrichshafen Ag, 7990 Friedrichshafen Tandempumpe

Patent Citations (4)

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Publication number Priority date Publication date Assignee Title
US2604047A (en) * 1945-09-19 1952-07-22 Hulman Two-stage hydraulic pressure pump
DE10117373A1 (de) * 2001-04-06 2002-10-10 Mannesmann Rexroth Ag Hydraulisches Pumpenaggregat
US7007468B1 (en) * 2003-06-27 2006-03-07 Hydro-Gear Limited Partnership Charge pump for a hydrostatic transmission
DE102004009838A1 (de) * 2004-02-28 2005-09-22 Zf Lenksysteme Gmbh Flügelzellenpumpe

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105484967A (zh) * 2014-10-07 2016-04-13 罗伯特·博世有限公司 带有主泵和辅助泵的泵装置

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