CN103597212A - Infinitely adjustable coolant pump - Google Patents
Infinitely adjustable coolant pump Download PDFInfo
- Publication number
- CN103597212A CN103597212A CN201280026098.7A CN201280026098A CN103597212A CN 103597212 A CN103597212 A CN 103597212A CN 201280026098 A CN201280026098 A CN 201280026098A CN 103597212 A CN103597212 A CN 103597212A
- Authority
- CN
- China
- Prior art keywords
- positioning disk
- impeller
- cooling medium
- medium pump
- opening
- Prior art date
- Legal status (The legal status 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 status listed.)
- Granted
Links
- 239000002826 coolant Substances 0.000 title claims abstract description 25
- 239000012530 fluid Substances 0.000 claims abstract description 21
- 238000002485 combustion reaction Methods 0.000 claims abstract description 6
- 238000001816 cooling Methods 0.000 claims abstract description 5
- 238000006073 displacement reaction Methods 0.000 claims description 13
- 238000000418 atomic force spectrum Methods 0.000 description 9
- 238000010586 diagram Methods 0.000 description 5
- 230000002153 concerted effect Effects 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000004891 communication Methods 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 230000003137 locomotive effect Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000012937 correction Methods 0.000 description 1
- 230000001970 hydrokinetic effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000001105 regulatory effect Effects 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
- 238000012360 testing method Methods 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D15/00—Control, e.g. regulation, of pumps, pumping installations or systems
- F04D15/0027—Varying behaviour or the very pump
- F04D15/0038—Varying behaviour or the very pump by varying the effective cross-sectional area of flow through the rotor
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D3/00—Axial-flow pumps
Abstract
The invention relates to a coolant pump for a cooling circuit of an internal combustion engine, comprising a pump housing (1) in which a drivable shaft (2a) is mounted, at the one end of which drivable shaft impeller (4) is fastened. Said impeller (4) has vanes (6) protruding into a suction chamber (7) and is connected to a cover plate (9). By the rotation of the impeller (4) in conjunction with the cover plate (9), fluid can be drawn into the suction chamber (7) via an intake connection (10) of the pump housing (1) and can be conveyed into the pump housing (1) via the vanes (6). A guide plate (12), which can be moved axially by means of an actuator unit (3), is arranged between the impeller (4) and the cover plate (9) and has a contour corresponding to the impeller (4) and a projection (13) oriented in the direction of the impeller (4). The coolant pump is characterized in that the guide plate (12) has at least one opening (11) and the impeller (4) has a closure contour (5) that points in the direction of the guide plate (12), wherein the closure contour (5) can be brought into engagement with one of the openings (11) of the guide plate (12) and closes said opening partially or completely.
Description
Technical field
The present invention relates to a kind of cooling medium pump with pump case of the cooling circuit for internal-combustion engine.At pump case internal support, have drivable axle, in the end of axle, be fixed with impeller, impeller has towards the blade of charging in suction chamber and is connected with shrouding disc.Due to the rotation of shrouding disc and the vaned impeller of tool, the suction pipe joint that makes fluid pass through pump case is inhaled in suction chamber and through blade and is further transported in pump case.Between impeller and shrouding disc, arranging and can pass through the positioning disk of regulation unit axial displacement.Positioning disk has the profile corresponding with impeller and towards the overhang of impeller.
Background technique
In order to realize the rapid heating of internal-combustion engine and to adjust targetedly engine temperature, cooling medium pump should be can break-make and be adjustable under the best circumstances.This realizes targetedly by adjusting discharge capacity.In order to set, carry stream or volume flow, at the positioning disk of impeller inside axially at pump intrinsic displacement.This must occur through actuator, this actuator as much as possible the medium ground of structure space, preferably build in the axial direction.According to the cooling medium pump of the above-mentioned type, by document DE102008046424A1, be disclosed.
Test shows, is applied to hydraulic resultant force that positioning disk applies and according to rotating speed, servo-positioning (Stellposition) and pump, implements to think and surpass 150N.This power demand must be applied by actuator, and this actuator is in the situation that all rotating speeds, temperature and repetition frequency degree must guarantee the correction of positioning disk.This situation depends on certain size or certain basic principle of relevant actuating mechanism.Due to this reason, application has the more expensive actuator of high structure space demand conventionally.
Summary of the invention
The present invention is based on following task, that is, provide a kind of can break-make or adjustable cooling medium pump, its actuator does not need extra cost or structure space to apply for regulating the power of positioning disk.
According to the present invention, this task is to solve like this, that is, positioning disk has at least one opening.By the opening existing, the effective pressure having reduced between positioning disk front side and positioning disk rear side is poor, and this has reduced again as making the needed axial force of positioning disk displacement.Alleviated the fluid communication between positioning disk front side and positioning disk rear side
the fluid being radially transferred after positioning disk has the typical centrifugal pressure of impeller.With after entering by hole, silt up together with part (Stauanteil) axially encountering occur on impeller rear wall certain, after positioning disk, produce a middle pressure.Therefore fluid under pressure has a component, and this component is directed in " closing positioning disk " direction.Direction has been described the axial displacement of positioning disk in shrouding disc direction " to close positioning disk ".This causes reduce making a concerted effort in " opening positioning disk " direction.Direction has been described the axial displacement of positioning disk in impeller direction " to open positioning disk ".Thus, actuator, in its locomotive function, is unloaded for the power that will apply.
Prove advantageously, in positioning disk, offer more than one opening.In this case, these openings have different shapes, for example for make full use of flow effect flow optimized shape and radially or be positioned at the opening extending on circumferencial direction on positioning disk, or the shape of optimizing for the production of more advantageously manufacturing.Do not rely on mode of execution ground, the effect of opening arranges it is in the close scope of positioning disk rotation axis the most fully.
In addition,, shown in the diagram of Fig. 4, fluid force depends on the aperture of positioning disk.In the ideal case, fluid force is zero, and thus, actuator can consume the earth's axis to mobile guide dish without additional power.For the positioning disk that there is no opening, from figure, learn, can not realize zero fluid force.Number of openings is higher, and force level declines just sooner.But this figure also illustrates, force level has negative sign from certain aperture of positioning disk and certain number of openings.Negative force level or negative fluid force mean, positioning disk is within the side of shrouding disc moves up and therefore fluid stream is suppressed to water pump.This will be avoided.Therefore, actuator can be applied in enough power and overcome negative fluid force, and actuator must be more powerful or size is larger, and this will cause additional cost again.
In order to stop this point, regulation unit can have spring alternatively.Spring makes positioning disk indirectly pass through axle at this and be applied in pressure in " opening positioning disk " direction.This mode of execution is a kind of fail-safe solution.When actuator lost efficacy and when positioning disk is pulled in " closing positioning disk " direction due to a negative fluid force, this causes the minimizing of flow of cooling medium, spring produces a back pressure, to prevent that positioning disk from closing.But in this embodiment, total force curve must be improved to the pre-tensioner so much of spring.Thus, the power of partly having offset again previous acquisition reduces.
In order to apply conventional and actuator cheaply, correspondingly the aperture of tuning positioning disk and the number of openings in positioning disk, be proved to be favourable.Thus, suppose to set a fluid force that acts on the 20N-50N of positioning disk, this fluid force is pressed positioning disk and is therefore opened cooling medium pump in impeller direction.Thus, should stop negative fluid force, this makes again the application of failure safe spring unnecessary.Therefore in of the present invention specializing, propose, impeller has the additional profile of closing, and this is closed profile and points to towards the direction of positioning disk, and closes profile and can engage with at least one opening of positioning disk and also partly or entirely close this opening.
In addition be set to, close profile and there is more than one closing element.Each closing element can differ from one another in their size (length, curvature, slope, diameter).
Closing element can be implemented taperedly, that is, closing element is tapered in the direction towards impeller towards shrouding disc.
Another feasibility of the present invention is, closing element is foliaceous to be implemented.For example as be disposed on impeller, be placed the falciform body with variable height in a circumferential direction or be positioned in addition the fin with variable height in the radial direction, they can directly be arranged on the blade of impeller again.
According to another decision design regulation of the present invention, regulation unit comprises actuator, and this actuator does not rely on the rotating speed of impeller and actuates.
Accompanying drawing explanation
Embodiments of the invention have been shown in Fig. 1 to Fig. 4, have below been described in detail, wherein, the present invention is not limited to these embodiments.In the accompanying drawings:
Fig. 1 illustrates sectional drawing that positioning disk is closed and offer adjustable cooling medium pump of opening in positioning disk;
Fig. 2 a illustrates the schematic diagram of the positioning disk that its opening do not close;
Fig. 2 b illustrates the schematic diagram of the positioning disk that its split shed closed by closing element (falciform body);
Fig. 2 c illustrates the schematic diagram of the positioning disk that its opening do not close;
Fig. 2 d illustrates the schematic diagram of the positioning disk that opening closed by closing element (fin);
Fig. 3 illustrates the detail drawing of the positioning disk of the closing element with taper; And
Fig. 4 illustrates the figure that depends on the number of openings of positioning disk and the different fluid force curve of aperture.
Embodiment
Fig. 1 illustrates the cooling medium pump for the cooling circuit of internal-combustion engine, and it has pump case 1.At pump case 1 internal support, there is drivable axle 2a, in an end of axle 2a, be fixed wtih impeller 4.Impeller 4 has towards the blade 6 of charging in suction chamber 7.Impeller 4 and shrouding disc 9 interconnect.When impeller 4 rotation, fluid is transported in suction chamber 7 through the suction pipe joint 10 of pump case 1.Between impeller 4 and shrouding disc 9, arranging and can pass through the positioning disk 12 of regulation unit 3 axial displacements.Positioning disk 12 has the profile corresponding with impeller 4 and towards the overhang 13 of the direction orientation of impeller 4.In order to realize the rapid heating of internal-combustion engine and to adjust targetedly engine temperature, cooling medium pump must be adjustable or can break-make.To this, meet demand and adjust volume flowrate.In order to adjust volume flowrate, positioning disk 12 is axially at pump case 1 intrinsic displacement.Between impeller 4 and shrouding disc 9, therefore the positioning disk 12 change apertures of internal displacement also control the circulation of volume flowrate.Regulation unit 3 not only comprises axle 2a and push rod 2b that can axial displacement in axle 2a, and comprises the actuator 14 of actuate push rods 2b.Push rod 2b forms and is directly connected with positioning disk 12.The displacement of positioning disk 12 is controlled by actuator 14.Actuator 14 as much as possible structure space is integrated in cooling medium pump mediumly.Due to this reason, need to be by due to volume flowrate, keep as far as possible littlely making a concerted effort on positioning disk 12, to also can select actuator 14 in the favourable mode of structure space.Can reduce now thus, to positioning disk 12 and the therefore force level to actuator 14, according to the present invention, in positioning disk 12, to offer opening 11.By offering opening 11, the effective pressure having reduced between positioning disk front side (towards the face of shrouding disc) and positioning disk rear side (face of impeller dorsad) is poor.This causes again hydrokinetic the reducing on positioning disk 12 that act on of volume flowrate.Therefore, alleviated the fluid communication between positioning disk front side and positioning disk rear side.In addition, by the fluid of radial delivery, at positioning disk rear side, produced a pressure pad.This pressure causes a force component in " closing positioning disk " direction, and this has reduced again making a concerted effort and thus actuator 14 being unloaded in its locomotive function in " opening positioning disk " direction.When positioning disk front side abuts on shrouding disc 9 and no longer has volume flowrate and flow, positioning disk 12 is closed.The aperture of positioning disk 12 is the signs of volume flowrate of cooling medium pump of flowing through.From the figure of Fig. 4, can find out the number of the opening 11 of offering, the aperture of positioning disk 12 and act on the association between the fluid force on positioning disk 12 in positioning disk 12.Along with the increase of opening 11 numbers, when the aperture of positioning disk 12 is identical, force curve declines.Yet from definite aperture, force curve partly rotates back into negative.This causes the masterpiece in " closing positioning disk " direction to be used for positioning disk 12, therefore needs a kind of " failure safe solution ".This means, as long as also need the cooling of motor, just mustn't by mistake close positioning disk 12.To this solution, be to use additional spring 8.This spring is encased in regulation unit 3 and acts on push rod 2b.This spring 8 must have pre-tensioner, thereby even positioning disk 12 was also got back to initial position through push rod 2b at the direction top offset of impeller 4 when actuator 14 loses efficacy.In order again to eliminate this negative power by so-called " failure safe spring ", must be around the total force curve of the pre-tensioner raising of this spring 8.This causes again the power realizing by opening 11 to reduce partly loss again.This causes using power actuator 14 powerful and that therefore occupy larger structure space.
As improvement project according to the present invention, therefore the opening 11 of the variable break-make that depends on aperture of positioning disk 12 is proposed.This realizes by closing profile 5, closes profile 5 and is loaded in the impeller 4 that is provided with blade 6.As shown in Figure 2 to Figure 3, this can be encased in the steel embedded piece of impeller 4 or extruding of impeller is sealed interior or also can be in the blade of impeller itself.By positioning disk 12 is moved axially in the direction of impeller 4, the closing element 5a that is foliaceous formation is engaged in one or more openings corresponding with it 11 and closes this opening 11.At Utopian force curve 20 shown in the figure shown in Fig. 4.Utopian force curve 20 shown to positioning disk 12 almost keep identical power effect, do not rely on its aperture.This Utopian force curve 20 only has when reaching the operation point S marking separately
xafter be just converted while "jump" to the operation point of nearest arrangement.This realizes by changing the number of opening 11 and the aperture of positioning disk 12 of positioning disk 12.
This stepless opening by the opening 11 of positioning disk 12 is changed, so as " soft " of realizable force level, stably, non-unexpected change.Non-unexpected adjustment is played positive role to the quality of the control/adjusting of positioning disk position, because can there is not unexpected power spring and the spring of position therefore.Based on closing the geometrical shape of profile 5 and the number of the opening 11 in positioning disk 12, can realize this open-minded without bouncing
So infinitely opening the particular design of opening 11 by closing element 5a realizes.Allow the conical in shape of being not only closing element of this point, and be its foliaceous shape highly raising.Closing element 5a is partly snapped in the opening 11 of the positioning disk 12 of axial displacement between impeller 4 and shrouding disc 9.Positioning disk 12 based on displacement and aperture is changed, and owing to closing profile 5 and also make partly or fully to open or close the opening 11 of different numbers.Fig. 2 b and Fig. 2 d are illustrated in open position the positioning disk 12 with the opening 11 of closing.This is in the drawings corresponding to from 100% aperture until the operating range of operation point S1.When positioning disk 12 is during further at " closing " direction top offset, opening 11 due to the closing element 5a highly raising by infinitely open-minded.Therefore more openings are little by little opened.This is in the drawings corresponding between the S1 to S2 of operation point and also have the operating range between the S2 to S3 of operation point.Fig. 2 a and Fig. 2 c show with positioning disk 12 opening 11 of not closing, under in off position.This is in the drawings according to aperture and corresponding to the operating range between operation point S3 to S4 or 0% aperture.
Reference numerals list
1 pump case
2a axle
2b push rod
3 regulation units
4 impellers
5 close profile
5a closing element
6 blades
7 suction chambers
8 springs
9 shrouding discs
10 suction pipe joints
11 openings
12 positioning disks
13 overhang
14 actuators
20 Utopian force curves
S1 operation point 1
S2 operation point 2
S3 operation point 3
Claims (9)
1. the cooling medium pump for the cooling circuit of internal-combustion engine, described cooling medium pump has pump case (1), at described pump case (1) internal support, there is drivable axle (2a), an end at described axle (2a) is fixed wtih impeller (4), described impeller (4) has towards the blade (6) of charging in suction chamber (7) and is connected with shrouding disc (9), wherein, by described impeller (4), rotate together with described shrouding disc (9), fluid can be inhaled into through the suction pipe joint (10) of described pump case (1) in described suction chamber (7) and can be transported in described pump case (1) through described blade (6), wherein, between described impeller (4) and described shrouding disc (9), arranging the positioning disk (12) that can pass through regulation unit (3) axial displacement, described positioning disk (12) has the profile corresponding with described impeller (4) and towards the overhang (13) of described impeller (4), it is characterized in that, described positioning disk (12) has at least one opening (11).
2. cooling medium pump according to claim 1, is characterized in that, described impeller (4) has the profile of closing (5), described in close profile (5) and point to described positioning disk (12).
3. cooling medium pump according to claim 2, is characterized in that, described in close profile (5) and can and partly or entirely close this opening with the interlock of one of the opening (11) of described positioning disk (12).
4. cooling medium pump according to claim 2, is characterized in that, described in close profile (5) and there is more than one closing element (5a), wherein, the size of described each closing element (5a) can differ from one another.
5. cooling medium pump according to claim 4, is characterized in that, described closing element (5a) is foliaceous to be implemented.
6. cooling medium pump according to claim 4, is characterized in that, described closing element (5a) is implemented taperedly.
7. according to the cooling medium pump described in claim 5 and 6, it is characterized in that, described in close stepless the closing that profile (5) has been realized described opening (11).
8. cooling medium pump according to claim 1, is characterized in that, described regulation unit (3) comprises actuator (14), and described actuator (14) does not rely on the rotating speed of described impeller (4) and actuates.
9. cooling medium pump according to claim 1, is characterized in that, described regulation unit (3) has spring (8), and described positioning disk (12) is by the adjusted initial position of getting back to of described spring (8).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102011077029A DE102011077029A1 (en) | 2011-06-07 | 2011-06-07 | Infinitely variable coolant pump |
| DE102011077029.1 | 2011-06-07 | ||
| PCT/EP2012/054515 WO2012167961A1 (en) | 2011-06-07 | 2012-03-15 | Infinitely adjustable coolant pump |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN103597212A true CN103597212A (en) | 2014-02-19 |
| CN103597212B CN103597212B (en) | 2016-03-30 |
Family
ID=45875946
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201280026098.7A Expired - Fee Related CN103597212B (en) | 2011-06-07 | 2012-03-15 | Infinitely variable cooling medium pump |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US20140003913A1 (en) |
| CN (1) | CN103597212B (en) |
| DE (1) | DE102011077029A1 (en) |
| WO (1) | WO2012167961A1 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102011077030A1 (en) * | 2011-06-07 | 2012-12-13 | Schaeffler Technologies AG & Co. KG | Adjustable coolant pump |
| CN103629121A (en) * | 2013-12-12 | 2014-03-12 | 兰州理工大学 | Dynamic axial force testing device for impeller of centrifugal pump |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4828455A (en) * | 1982-12-21 | 1989-05-09 | Aisin Seiki Kabushiki Kaisha | Temperature responsive blade shroud-disk for thermostatic water pump |
| DE9200240U1 (en) * | 1992-01-11 | 1992-02-27 | Kultscher, Armin Henry, 3300 Braunschweig, De | |
| US5169286A (en) * | 1989-03-09 | 1992-12-08 | Yutaka Yamada | Variable capacity centrifugal water pump with movable pressure chamber formed by impeller |
| US5800120A (en) * | 1995-11-07 | 1998-09-01 | A. W. Chesterton Co. | Pump impeller with adjustable blades |
| US6074167A (en) * | 1999-02-05 | 2000-06-13 | Woodward Governor Company | Variable geometry centrifugal pump |
| CN101233338A (en) * | 2005-08-01 | 2008-07-30 | 蒂姆肯公司 | Coolant pump for internal combustion engine |
| CN101253314A (en) * | 2005-08-30 | 2008-08-27 | 弗洛沃克第二系统有限责任公司 | Automotive coolant pump apparatus |
| DE102008046424A1 (en) * | 2008-09-09 | 2010-03-11 | Schaeffler Kg | Adjustable coolant pump |
| CN103688061A (en) * | 2011-06-07 | 2014-03-26 | 谢夫勒科技股份两合公司 | Controllable coolant pump |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2255503A1 (en) * | 1972-11-13 | 1974-05-16 | Heinz Knebel | DEVICE FOR CONTINUOUSLY ADJUSTABLE EMISSION VOLUME CONTROL FOR CENTRIFUGAL PUMPS, FANS AND BLOWERS |
| JPH0622160Y2 (en) * | 1986-09-30 | 1994-06-08 | 三菱自動車工業株式会社 | pump |
| DE19901123A1 (en) * | 1999-01-14 | 2000-07-20 | Bosch Gmbh Robert | Controllable radial pump, especially for supplying coolant for car has adjuster connected with sleeve which can be slid over pump blades in axial direction |
-
2011
- 2011-06-07 DE DE102011077029A patent/DE102011077029A1/en not_active Withdrawn
-
2012
- 2012-03-15 US US14/004,803 patent/US20140003913A1/en not_active Abandoned
- 2012-03-15 CN CN201280026098.7A patent/CN103597212B/en not_active Expired - Fee Related
- 2012-03-15 WO PCT/EP2012/054515 patent/WO2012167961A1/en active Application Filing
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4828455A (en) * | 1982-12-21 | 1989-05-09 | Aisin Seiki Kabushiki Kaisha | Temperature responsive blade shroud-disk for thermostatic water pump |
| US5169286A (en) * | 1989-03-09 | 1992-12-08 | Yutaka Yamada | Variable capacity centrifugal water pump with movable pressure chamber formed by impeller |
| DE9200240U1 (en) * | 1992-01-11 | 1992-02-27 | Kultscher, Armin Henry, 3300 Braunschweig, De | |
| US5800120A (en) * | 1995-11-07 | 1998-09-01 | A. W. Chesterton Co. | Pump impeller with adjustable blades |
| US6074167A (en) * | 1999-02-05 | 2000-06-13 | Woodward Governor Company | Variable geometry centrifugal pump |
| CN101233338A (en) * | 2005-08-01 | 2008-07-30 | 蒂姆肯公司 | Coolant pump for internal combustion engine |
| CN101253314A (en) * | 2005-08-30 | 2008-08-27 | 弗洛沃克第二系统有限责任公司 | Automotive coolant pump apparatus |
| DE102008046424A1 (en) * | 2008-09-09 | 2010-03-11 | Schaeffler Kg | Adjustable coolant pump |
| CN103688061A (en) * | 2011-06-07 | 2014-03-26 | 谢夫勒科技股份两合公司 | Controllable coolant pump |
Also Published As
| Publication number | Publication date |
|---|---|
| CN103597212B (en) | 2016-03-30 |
| US20140003913A1 (en) | 2014-01-02 |
| DE102011077029A1 (en) | 2012-12-13 |
| WO2012167961A1 (en) | 2012-12-13 |
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Owner name: SCHAEFFLER FIFTH INVESTMENT MANAGEMENT GMBH + CO., Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES GMBH + CO. KG Effective date: 20150728 |
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Address after: German Herzogenaurach Applicant after: SCHAEFFLER TECHNOLOGIES AG & CO. KG Address before: German Herzogenaurach Applicant before: SCHAEFFLER TECHNOLOGIES GmbH & Co.KG Address after: German Herzogenaurach Applicant after: SCHAEFFLER TECHNOLOGIES GmbH & Co.KG Address before: German Herzogenaurach Applicant before: Fifth Schaeffler investment management GmbH & Co.KG |
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Free format text: CORRECT: ADDRESS; FROM: Free format text: CORRECT: APPLICANT; FROM: SCHAEFFLER FIFTH INVESTMENT MANAGEMENT GMBH + CO., KG TO: SCHAEFFLER TECHNOLOGIES GMBH + CO. KG Free format text: CORRECT: APPLICANT; FROM: SCHAEFFLER TECHNOLOGIES GMBH + CO. KG TO: SCHAEFFLER TECHNOLOGY GMBH + CO. KG |
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