WO2007128257A1 - Fördereinrichtung für ein fluid - Google Patents
Fördereinrichtung für ein fluid Download PDFInfo
- Publication number
- WO2007128257A1 WO2007128257A1 PCT/DE2007/000683 DE2007000683W WO2007128257A1 WO 2007128257 A1 WO2007128257 A1 WO 2007128257A1 DE 2007000683 W DE2007000683 W DE 2007000683W WO 2007128257 A1 WO2007128257 A1 WO 2007128257A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- conveyor
- gerotor
- drive
- conveying device
- rotor
- Prior art date
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
- 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
- F04C15/00—Component parts, details or accessories of machines, pumps or pumping installations, not provided for in groups F04C2/00 - F04C14/00
- F04C15/0057—Driving elements, brakes, couplings, transmission specially adapted for machines or pumps
- F04C15/0061—Means for transmitting movement from the prime mover to driven parts of the pump, e.g. clutches, couplings, transmissions
-
- 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
- F04C2/086—Carter
-
- 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
- F04C2230/00—Manufacture
- F04C2230/60—Assembly methods
- F04C2230/603—Centering; Aligning
Definitions
- the invention relates to a conveying device, in particular a gerotor pump, for a fluid, in particular a cooling fluid, with a drive plane in which a drive device cooperates with a displacement device, in particular a gerotor external rotor, and with a Anflanschebene in which the conveyor to a mounting surface is flanged.
- the object of the invention is to provide an improved conveyor for a fluid, in particular a shorter-built conveyor.
- the object is in a conveying device, in particular a gerotor pump, for a fluid, in particular a cooling fluid having a drive plane, in which a drive means cooperates with a displacement device, in particular a gerotor outer rotor, and with a Anflanschebene in which the conveyor to a mounting surface is flanged, achieved by the drive plane is spaced from the Anflanschebene.
- a conveying device for a fluid, in particular a cooling fluid having a drive plane
- a drive means cooperates with a displacement device, in particular a gerotor outer rotor, and with a Anflanschebene in which the conveyor to a mounting surface is flanged, achieved by the drive plane is spaced from the Anflanschebene.
- a preferred embodiment of the conveyor is characterized in that the gerotor outer rotor has an external toothing, which cooperates with the drive means.
- the drive device may comprise, for example, an internal combustion engine, wherein the drive device may be associated with a shaft of a drive train coupled to the internal combustion engine.
- the internal combustion engine can thus drive the conveyor via parts of the drive train.
- the conveyor can thereby convey a fluid, in particular a cooling fluid.
- a coupling device of the drive train can be cooled by the fluid.
- the gerotor outer rotor has a cylindrical bearing surface.
- the bearing surface can cooperate with a corresponding surface, for example a cylindrical surface of a housing of the conveyor, whereby a radial bearing for the gerotor external rotor can be realized.
- the cylindrical bearing surface is arranged adjacent to the external toothing.
- a further preferred embodiment of the conveyor is characterized in that the diameter of the top circle of the external toothing is equal to or smaller than the diameter of the cylindrical bearing surface. This makes it possible, for example for the assembly of the gerotor external rotor, push the external toothing through the cylindrical inner surface.
- the conveyor is characterized in that it comprises a housing.
- the housing can receive the components of the conveyor and store accordingly, for example, the gerotor external rotor.
- the housing may have the cylindrical bearing surface.
- a further preferred embodiment of the conveyor is characterized in that the housing has a pump tufting.
- the pump tufting can be designed to receive the gerotor outer rotor essentially in a form-fitting manner and to support it in a rotatable manner.
- the Pumpentopfung a cylindrical shape, which is adapted to the cylindrical bearing surface of the gerotor outer rotor, for example as a clearance fit. Due to the size ratios of the cylindrical bearing surface to the tip circle of the external toothing, it is possible to arrange the external toothing at the bottom of the pump tufting. Corresponding kidney-shaped openings of inflow and outflow channels through which the fluid can be conveyed open into the pumping sump.
- a further preferred embodiment of the conveyor is characterized in that the pump tufting is formed hollow cylindrical.
- the gerotor external rotor can be introduced into the hollow cylinder of the pump tubing.
- a further preferred exemplary embodiment of the delivery device is characterized in that the pumping unit has a kidney-shaped opening of an inlet channel as well as a kidney-shaped opening of an outlet channel. Through the channels, the fluid can be promoted be so sucked through the opening of the inlet channel into the pump chamber within the pump dpfopfung and out through the opening of the outlet channel out again.
- a further preferred embodiment of the conveyor is characterized in that the pump plug has an opening in which the drive means meshes with the external toothing of the gerotor outer rotor.
- the pumping or the housing of the conveyor is locally opened radially, preferably exactly in the width of the outer toothing of the gerotor outer rotor. This makes it possible to carry out the power flow or the rotational drive for the gerotor outer rotor through the opening.
- a part of the drive means engage in the conveyor until the toothing of the gerotor outer rotor, without thereby affecting the radial bearing means of the cylindrical bearing surface in the pump tufting.
- Another preferred embodiment of the conveyor is characterized in that the opening is spaced from the Anflanschebene. This makes it possible to arrange the drive device, in particular the parts which extend through the opening, also spaced from the flange plane.
- a further preferred embodiment of the conveying device is characterized in that the drive device has a pinion spaced from the Anflanschebene.
- the pinion can drive the gerotor outer rotor.
- a further preferred embodiment of the conveyor is characterized in that the pinion of a drive shaft, in particular a crankshaft, is assigned.
- the drive shaft or crankshaft may be part of the drive device via which ultimately the required energy for driving the conveyor can be provided.
- the drive means comprises a meshing with the pinion and with the external teeth of the gerotor outer rotor intermediate gear.
- the energy can be transmitted to drive the conveyor.
- a certain radial distance can be overcome, and / or a translation for the gerotor external rotor can be adjusted. Consequently, the rotational speed of the gerotor external rotor can thus be adjusted in relation to the rotational speed of the drive device.
- the intermediate wheel thereby changes the direction of rotation of the gerotor outer rotor.
- a - the position of the conveyor for example, relative to the drive shaft or output shaft of the drive device, are set.
- Another preferred embodiment of the conveyor is characterized in that the pinion meshes directly with the outer toothing of the gerotor outer rotor. In this case, can be dispensed with the intermediate gear, whereby a comparatively close to the axis position of the conveyor can be realized.
- a further preferred embodiment of the conveyor is characterized in that the gerotor outer rotor has a first end face and a second end face, wherein the first end face are axially mounted on a base of the pump tufting and the second end face on the Anflanschebene.
- Another preferred embodiment of the conveyor is characterized in that the second end face is axially mounted on a sealing layer. It is possible to provide the Anflanschebene with an additional sealing layer.
- the sealing layer can make up the entire surface of the flange plane covered by the conveying device, as a result of which the conveying device can be flanged to the flange plane in a fluid-tight manner.
- the housing of the conveyor can thus be realized only with a housing half-shell and the flat surface applied to the Anflanschebene sealing surface. A second housing half shell is not required.
- Another preferred embodiment of the conveyor is characterized in that the sealing layer between the housing and the Anflanschebene is arranged.
- the sealing layer can be sealed fluid-tight to the environment.
- a further preferred embodiment of the conveyor device is characterized in that a gear of the drive device has the Anflanschebene.
- the drive means comprises an internal combustion engine. The internal combustion engine can provide the energy required to drive the conveyor.
- a further preferred embodiment of the conveyor is characterized in that the transmission and the internal combustion engine are parts of a drive train of a motor vehicle.
- the conveyor can therefore be integrated into a motor vehicle.
- a further preferred embodiment of the conveyor is characterized in that the drive train has a coupling device, wherein the coupling device is supplied by the conveyor with the fluid.
- fluid-cooled coupling devices can switch higher torque and / or energy flows.
- a further preferred embodiment of the conveyor is characterized in that the coupling device has a wet-running double clutch in lamellar construction.
- Wet-running double clutches can transmit or switch particularly large energy flows and / or torque flows.
- Another preferred embodiment of the conveyor is characterized in that the conveyor has a bearing for the intermediate gear.
- the conveyor has a bearing for the intermediate gear.
- a further preferred embodiment of the conveyor is characterized in that the housing has a partial enlargement for the bearing of the intermediate gear.
- the partial enlargement of the housing can be made as small as possible, so that results in the lowest possible total weight of the conveyor and yet the function of a bearing for the intermediate gear can be provided.
- a further preferred embodiment of the conveyor is characterized in that it has a gerotor inner rotor meshing with the gerotor outer rotor.
- the gerotor internal rotor can be driven via the gerotor external rotor and so realize together with the gerotor external rotor necessary for the fluid pump pump chambers.
- a further preferred embodiment of the conveyor is characterized in that the gerotor inner rotor is mounted radially on the housing, in particular has a bearing pin engaging with the housing. The bearing can absorb the pressure forces necessary for fluid conveyance, which act on the gerotor inner rotor.
- the axial bearing analogous to the gerotor outer rotor, that is done on the Anflanschebene or the sealing layer and on the base of the pump tufting.
- the object is also achieved with a clutch device, in particular multi-disc clutch device, in particular dual clutch device, for torque transmission between a motor and a transmission, which is drivingly connected to a previously described conveyor, that the fluid is conveyed from the conveyor to the coupling device.
- a clutch device in particular multi-disc clutch device, in particular dual clutch device, for torque transmission between a motor and a transmission, which is drivingly connected to a previously described conveyor, that the fluid is conveyed from the conveyor to the coupling device.
- the object is achieved in a drive train with an internal combustion engine and a coupling device by a previously described conveyor.
- Figure 1 is a sectional view of a known from the prior art redesignate device together with a drive device partially shown;
- Figure 2 is a sectional view of a conveyor according to the invention with an intermediate gear
- Figure 3 is a sectional view of another conveyor without intermediate gear
- characters 4 and 5 show various three-dimensional detail views of a housing of a Fluid Eatein direction
- FIG. 6 shows a three-dimensional representation of a gerotor external rotor of deliberatelyeinrichtun gene according to Figures 2-4.
- the conveyor 1 shows a sectional view of a known from the prior art conveyor 1.
- the conveyor 1 is partially shown together with a drive device 3, which is only partially shown.
- the conveyor 1 has a housing 5 with an upper half-shell 7 and a lower half-shell 9.
- the half shells 7 and 9 are joined together along a flanging plane 11.
- the lower half shell 9 is fixed in a planar manner via a sealing layer 13 at a sealing plane 15.
- the sealing plane 15 is part of an outer wall of a gearbox 17 of the drive device 3.
- the drive device 3 may be an internal combustion engine together with the associated drive train, for example a transmission, a rotational vibration damping device and a clutch device comprising - in each case not shown here - act.
- the conveyor 1 may be designed as an internal gear pump for conveying a cooling fluid for the coupling device, not shown.
- the conveyor device 1 is a gerotor pump with a gerotor external rotor 19 and a gerotor internal rotor 21.
- the gerotor external rotor 19 has a collar 23 which lies centrally in a drive plane 25, wherein the drive plane 25 with the Anflanschebene 11 coincides.
- the collar 23 of the gerotor external rotor 19 has an external toothing, which meshes with an intermediate gear 27 of the drive device 3.
- the intermediate gear 27 also meshes with a pinion 29 which is associated with a drive element 31 of the drive device 3.
- the drive element 31 drives the pinion 29, the pinion 29, the intermediate gear 27 and finally the intermediate gear 27 to the gerotor external rotor 19 at.
- the gerotor external rotor 19 in turn drives the gerotor internal rotor 21, so that it can promote the fluid.
- FIG. 2 shows an exemplary embodiment of a conveying device 1 according to the invention analogous to the conveying device 1, as shown in FIG.
- the exemplary embodiment in particular the differences from the prior art, will be explained in more detail below.
- the conveyor 1 according to Figure 2 has no lower half-shell. Rather, the upper half-shell 7 of the conveyor 1 is connected directly to the sealing plane 15 of the gearbox 17. In the illustration according to FIG. 2, therefore, the sealing plane 15 and the flange plane 11 coincide. It can be seen that the drive plane 25 and the flange 11 are spaced from each other.
- the sealing layer 13 according to the prior art as shown in Fig.
- the intermediate gear 27 engages through a recess 33 of the upper half shell 7 of the housing 5.
- the gerotor external rotor 19 in the width of the recess 33 and in the width of the intermediate gear 27 has an external toothing 35.
- the top circle of the external toothing 35 has the same or optionally a smaller diameter as a cylindrical outer surface 37 of the gerotor external rotor 19.
- the cylindrical outer surface 37 abuts against a cylindrical inner surface 39 of a pumping cup 41 of the upper half shell 7 of the housing 5 of the conveyor 1.
- the gerotor external rotor 19 is rotatably supported radially in the pumping plug 41 along a rotation axis 53. Furthermore, the gerotor outer rotor 19 has an upper end face 43 which abuts against a base 47 of the pumping sump 41. On the opposite side, that is on the lower end face 45, the gerotor external rotor 19 strikes against the sealing layer 13. Consequently, the gerotor outer rotor 19 is mounted within the pumping sump 41 axially by abutting its end faces 43 and 45 on the pumping sump 41 or the sealing layer 13. According to the principle of operation of a gerotor pump, the axes of rotation of the gerotor external rotor and the gerotor internal rotor are axially offset from one another.
- the conveyor 1 has pump chambers 49, which can convey a fluid via kidney-shaped opened channels 51, for example an outlet channel and an inlet channel.
- the pumped fluid can be supplied to a coupling device, not shown here for cooling.
- the gerotor inner rotor 21 is rotatably supported by means of a bearing pin 57 engaging in a blind hole 55 of the upper half-shell 7 of the housing 5.
- the principle of gerotor pumps is known, so that will not be discussed further here.
- the gerotor outer rotor 19 has no collar 23.
- the external toothing 35 is an integral part of the gerotor external rotor 19.
- the intermediate gear 27 is mounted on the upper half shell 7 of the housing 5 of the conveyor 1 as shown in Figure 2 radially rotatable.
- a bore 59 of the upper half-shell 7 of the housing 5 has a bearing pin 61.
- the bearing of the intermediate gearwheel 27 takes place on the lower half shell 9. It can be seen that valuable axial space is thereby consumed.
- FIG. 3 shows a sectional view of another conveyor 1, but without intermediate gear (27 in Figure 2). Identical parts are provided with the same reference numerals. For clarity, not all reference numerals are shown. In the following, only the differences from FIG. 2 will be discussed.
- the conveyor 1 according to Figure 3 In contrast to the conveyor 1 according to Figure 2, the conveyor 1 according to Figure 3, no intermediate gear 27 on.
- the pinion 29 meshes through the recess 33 of the housing 5 of the conveyor 1 through directly with the external teeth 35 of the gerotor external rotor 19.
- the upper half shell 7 of the housing 5 of Conveyor 1 be designed more compact.
- the upper half-shell 7 of the housing 5 has a partial enlargement 63, which serves to support the intermediate gear 27, so the bore 59 and the bearing pin 61 has.
- the partial enlargement 63 can be dispensed with according to FIG. 3.
- Figures 4 and 5 each show three-dimensional views of the upper half-shell 7 of the housing 5 of the conveyor 1, each obliquely on the Anflanschebene 11 of the upper half-shell 7 of the housing 5. It can be seen the recess 33 which opens the Pumpenentopfung 41 radially.
- the recess 33 has a first bearing surface 65 and a second bearing surface 67, which is used for example for the axial mounting of the intermediate gear 27 can be. Also visible is the radial enlargement 63 with the bore 59 for the bearing pin 61 for the radial mounting of the intermediate gear 27.
- different channels 51 in particular kidney-shaped openings 69 of the channels 51 in the base 47 of the pumping 41 can be seen.
- the upper half shell 7 of the housing 5 of the conveyor 1 has various holes 71 for flanging the conveyor 1 on a flat surface, for example, the outer surface of the gear box 17, on.
- FIG. 6 shows a three-dimensional view obliquely from the front of the gerotor external rotor 19 of the conveyor device 1 according to FIGS. 2-4.
- the cylindrical outer surface 37 which has the same external diameter as the external toothing 35 of the gerotor external rotor 19, can be seen.
- External rotor 19 also has an internal toothing 73, which meshes in the installed state with an external toothing 77 of the gerotor inner rotor 21.
- the internal toothing 73 of the gerotor external rotor 19 serves to drive the gerotor inner rotor 21 and to form the pump chambers 49.
- the conveyor 1 can be used for the transfer of oil for lubrication and cooling.
- the conveyor 1 must be designed only for a low maximum pressure. This means that the mechanical stress on the components, in particular the gerotor rotor 19 and 21 is low.
- the upper half-shell 7 of the housing 5 of the conveyor 1 has a bore 75.
- the bore 75 is designed for receiving a suction control valve of the conveyor 1.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary Pumps (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112007000940T DE112007000940A5 (de) | 2006-05-06 | 2007-04-19 | Fördereinrichtung für ein Fluid |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102006021219 | 2006-05-06 | ||
DE102006021219.3 | 2006-05-06 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2007128257A1 true WO2007128257A1 (de) | 2007-11-15 |
Family
ID=38290184
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/DE2007/000683 WO2007128257A1 (de) | 2006-05-06 | 2007-04-19 | Fördereinrichtung für ein fluid |
Country Status (2)
Country | Link |
---|---|
DE (1) | DE112007000940A5 (de) |
WO (1) | WO2007128257A1 (de) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010006575A2 (de) * | 2008-07-16 | 2010-01-21 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Verdrängermaschine |
Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE669696C (de) * | 1939-01-02 | Ludwig Geb | Zahnradpumpe mit Inneneingriff der Verzahnung | |
DE2717824A1 (de) * | 1976-04-22 | 1977-11-03 | Automobilove Zavody Np | Reversible verdraengerpumpe |
GB2020361A (en) * | 1978-05-08 | 1979-11-14 | Gen Motors Corp | Engine lubricating oil pump |
US5395217A (en) * | 1991-06-07 | 1995-03-07 | Schwabische Huttenwerke Gmbh | Gear pump for oil for an internal-combustion engine, in particular for motor vehicles |
DE29710407U1 (de) * | 1996-11-12 | 1997-07-31 | Voith Turbo Kg | Innenzahnradpumpe mit Antrieb über das Hohlrad |
WO2001038739A1 (de) * | 1999-11-24 | 2001-05-31 | Robert Bosch Gmbh | Vorrichtung zur reduzierung der axialkrafbelastung einer ein fluid fördernden pumpe |
EP1150014A2 (de) * | 2000-04-27 | 2001-10-31 | Man Nutzfahrzeuge Ag | Innenzahnradölpumpe |
DE202006000110U1 (de) * | 2006-01-04 | 2006-04-20 | Com Engineering Gmbh | Ölpumpe mit integriertem Getiebe |
WO2006134337A1 (en) * | 2005-06-11 | 2006-12-21 | Concentric Vfp Ltd | A variable output pump |
-
2007
- 2007-04-19 WO PCT/DE2007/000683 patent/WO2007128257A1/de active Application Filing
- 2007-04-19 DE DE112007000940T patent/DE112007000940A5/de not_active Withdrawn
Patent Citations (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE669696C (de) * | 1939-01-02 | Ludwig Geb | Zahnradpumpe mit Inneneingriff der Verzahnung | |
DE2717824A1 (de) * | 1976-04-22 | 1977-11-03 | Automobilove Zavody Np | Reversible verdraengerpumpe |
GB2020361A (en) * | 1978-05-08 | 1979-11-14 | Gen Motors Corp | Engine lubricating oil pump |
US5395217A (en) * | 1991-06-07 | 1995-03-07 | Schwabische Huttenwerke Gmbh | Gear pump for oil for an internal-combustion engine, in particular for motor vehicles |
DE29710407U1 (de) * | 1996-11-12 | 1997-07-31 | Voith Turbo Kg | Innenzahnradpumpe mit Antrieb über das Hohlrad |
WO2001038739A1 (de) * | 1999-11-24 | 2001-05-31 | Robert Bosch Gmbh | Vorrichtung zur reduzierung der axialkrafbelastung einer ein fluid fördernden pumpe |
EP1150014A2 (de) * | 2000-04-27 | 2001-10-31 | Man Nutzfahrzeuge Ag | Innenzahnradölpumpe |
WO2006134337A1 (en) * | 2005-06-11 | 2006-12-21 | Concentric Vfp Ltd | A variable output pump |
DE202006000110U1 (de) * | 2006-01-04 | 2006-04-20 | Com Engineering Gmbh | Ölpumpe mit integriertem Getiebe |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010006575A2 (de) * | 2008-07-16 | 2010-01-21 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Verdrängermaschine |
WO2010006575A3 (de) * | 2008-07-16 | 2010-08-05 | Luk Lamellen Und Kupplungsbau Beteiligungs Kg | Verdrängermaschine |
Also Published As
Publication number | Publication date |
---|---|
DE112007000940A5 (de) | 2009-01-22 |
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