CN103597212B - Infinitely variable cooling medium pump - Google Patents
Infinitely variable cooling medium pump Download PDFInfo
- Publication number
- CN103597212B CN103597212B CN201280026098.7A CN201280026098A CN103597212B CN 103597212 B CN103597212 B CN 103597212B CN 201280026098 A CN201280026098 A CN 201280026098A CN 103597212 B CN103597212 B CN 103597212B
- Authority
- CN
- China
- Prior art keywords
- positioning disk
- impeller
- cooling medium
- opening
- profile
- 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.)
- Expired - Fee Related
Links
- 239000002826 coolant Substances 0.000 title claims abstract description 22
- 239000012530 fluid Substances 0.000 claims abstract description 21
- 238000006073 displacement reaction Methods 0.000 claims abstract description 13
- 238000002485 combustion reaction Methods 0.000 claims abstract description 6
- 238000001816 cooling Methods 0.000 claims abstract description 5
- 238000004804 winding Methods 0.000 claims abstract description 4
- 238000000418 atomic force spectrum Methods 0.000 description 9
- 238000010586 diagram Methods 0.000 description 6
- 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
- 238000012937 correction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 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
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
- F04D3/00—Axial-flow pumps
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The present invention relates to a kind of cooling medium pump of the cooling circuit for internal-combustion engine, it has pump case (1), drivable axle (2a) at pump case (1) internal support, impeller (4) at an end winding support of axle (2a), impeller (4) has the blade (6) charged in suction chamber (7) and is connected with shrouding disc (9).Rotated together with shrouding disc (9) by impeller (4), the suction pipe joint (10) making fluid can be passed through pump case (1) to be drawn in suction chamber (7) and to can be passed through blade (6) and is transported in pump case (1).Between impeller (4) and shrouding disc (9), arrange the positioning disk (12) by regulation unit (3) axial displacement, positioning disk (12) has the profile corresponding with impeller (4) and the overhang (13) towards the direction orientation of impeller (4).It is characterized in that, positioning disk (12) has at least one opening (11), and impeller (4) has the closedown profile (5) of sensing positioning disk (12), and wherein, close profile (5) to be engaged with in the opening of positioning disk (12) (11), and partly or entirely close this opening.
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.Have drivable axle at pump case internal support, have impeller at the end winding support of axle, impeller has the blade charged in suction chamber and is connected with shrouding disc.Due to the rotation of shrouding disc and the vaned impeller of tool, fluid is made to be inhaled in suction chamber through the suction pipe joint of pump case and to be transported to further in pump case through blade.The positioning disk by regulation unit axial displacement is arranged between impeller and shrouding disc.Positioning disk has the profile corresponding with impeller and the overhang towards impeller.
Background technique
In order to realize the rapid heating of internal-combustion engine and adjust engine temperature targetedly, cooling medium pump should be can break-make and be adjustable under the best circumstances.This is realized targetedly by adjustment discharge capacity.In order to set conveying stream or volume flow, at the positioning disk of impeller internal axially at pump intrinsic displacement.This has to pass through actuator and occurs, and this actuator as much as possible structure space builds mediumly, preferably in the axial direction.Cooling medium pump according to the above-mentioned type is disclosed by document DE102008046424A1.
Test shows, the hydraulic resultant force being applied to positioning disk applying is implemented can think more than 150N according to rotating speed, servo-positioning (Stellposition) and pump.This power demand must be applied by actuator, and this actuator must ensure the correction of positioning disk when all rotating speeds, temperature and repetition frequency degree.This situation depends on certain size about actuating mechanism or certain basic principle.Due to this reason, application has the actuator costly of high structure space demand usually.
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 be applied for regulating the power of positioning disk.
According to the present invention, this task solves like this, that is, positioning disk has at least one opening.By the opening existed, the effective pressure between decreasing on front side of positioning disk and on rear side of positioning disk is poor, turn, this reduces the axial force for making required for positioning disk displacement.Fluid communication between alleviating on front side of positioning disk and on rear side of positioning disk
after positioning disk, the radial fluid be transferred has the typical centrifugal pressure of impeller.With silt up together with part (Stauanteil) axially encountering impeller rear wall occurs certain after entering in passing hole, after positioning disk, produce a middle pressure.Therefore the fluid be under pressure has a component, and this component is directed on " closedown positioning disk " direction." closedown positioning disk " direction depicts the axial displacement of positioning disk on shrouding disc direction.This causes reduce making a concerted effort on " opening positioning disk " direction.Direction depicts the axial displacement of positioning disk on 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, such as in order to make full use of the shape of the flow optimized of flow effect and radial direction or the opening extended on positioning disk that is positioned at circumferentially, or the shape of Optimizing manufacture in order to more advantageously manufacture.Do not rely on mode of execution ground, the effect of opening arranges it is in the scope near 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 not having opening, learn from figure, the fluid force of zero can not be realized.Number of openings is higher, and force level declines faster.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 moves up in the side of shrouding disc and therefore suppressed within water pump by fluid stream.This will be avoided.Therefore, actuator can be applied in enough power to overcome negative fluid force, actuator must more powerful or size larger, this will cause additional cost again.
In order to stop this point, regulation unit can have spring alternatively.Spring makes positioning disk indirectly on " opening positioning disk " direction, be applied in pressure through axle at this.This mode of execution is a kind of fail-safe solution.When actuator lost efficacy and positioning disk is pulled on " closedown positioning disk " direction due to a negative fluid force, this caused the minimizing of cooling medium stream, and spring produces a back pressure, to prevent positioning disk from closing.But in this embodiment, total force curve must be improved the pre-tensioner so much of spring.Thus, partly counteract again the power previously obtained to reduce.
In order to apply the actuator of conventional and low cost, the number of openings correspondingly in the aperture of tuning positioning disk and positioning disk, is proved to be favourable.Thus, suppose that setting one acts on the fluid force of the 20N-50N of positioning disk, this fluid force presses positioning disk and therefore opens cooling medium pump on impeller direction.Thus, should stop negative fluid force, this makes again the application of failsafe springs unnecessary.Therefore propose in of the present invention specializing, impeller has additional closedown profile, and this closedown profile 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 be upper different from each other in their size (length, curvature, slope, diameter).
Closing element can be implemented taperedly, that is, closing element is being tapered on the direction of shrouding disc towards impeller.
Another feasibility of the present invention is, closing element is that foliaceous ground is implemented.Such as being disposed in the fin with variable height on impeller, that be positioned in the falciform body with variable height circumferentially or be positioned in addition 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 that positioning disk is closed and in positioning disk, offers the sectional drawing of adjustable cooling medium pump of opening;
Fig. 2 a illustrates the schematic diagram of the positioning disk that its opening is not closed;
Fig. 2 b illustrates the schematic diagram of the positioning disk that its split shed is closed by closing element (falciform body);
Fig. 2 c illustrates the schematic diagram of the positioning disk that its opening is not closed;
Fig. 2 d illustrates the schematic diagram of the positioning disk that opening is 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 of the different fluid force curve of number of openings and the aperture depending on positioning disk.
Embodiment
Fig. 1 illustrates the cooling medium pump of the cooling circuit for internal-combustion engine, and it has pump case 1.There is drivable axle 2a at pump case 1 internal support, impeller 4 at an end winding support of axle 2a.Impeller 4 has the blade 6 charged in suction chamber 7.Impeller 4 and shrouding disc 9 are interconnected.When impeller 4 rotates, fluid is transported in suction chamber 7 through the suction pipe joint 10 of pump case 1.The positioning disk 12 by regulation unit 3 axial displacement is arranged between impeller 4 and shrouding disc 9.Positioning disk 12 has the overhang 13 of the profile corresponding with impeller 4 and the direction orientation towards impeller 4.In order to realize the rapid heating of internal-combustion engine and adjust engine temperature targetedly, cooling medium pump must be adjustable or can break-make.To this, adjust volume flowrate with meeting demand.In order to adjust volume flowrate, positioning disk 12 is axially at pump case 1 intrinsic displacement.Between impeller 4 and shrouding disc 9, the positioning disk 12 of internal displacement changes aperture and therefore controls the circulation of volume flowrate.Regulation unit 3 not only comprises axle 2a and can the push rod 2b of axial displacement in axle 2a, and comprises the actuator 14 of actuate push rods 2b.Push rod 2b is formed with positioning disk 12 and is directly connected.The displacement of positioning disk 12 is controlled by actuator 14.Actuator 14 should be integrated in cooling medium pump by structure space as much as possible mediumly.Due to this reason, need keep as far as possible little making a concerted effort due to volume flowrate on positioning disk 12, also actuator 14 can be selected in the mode that structure space is favourable.Can reduce now thus, to positioning disk 12 and therefore to the force level of actuator 14, according to the present invention, in positioning disk 12, to offer opening 11.By offering opening 11, the effective pressure reduced on front side of positioning disk on rear side of (face towards shrouding disc) and positioning disk between (dorsad the face of impeller) is poor.This causes again the hydrokinetic reduction acted on positioning disk 12 of volume flowrate.Therefore, the fluid communication between alleviating on front side of positioning disk and on rear side of positioning disk.In addition, on rear side of positioning disk, a pressure pad is produced by the fluid of radial delivery.This pressure causes a force component on " closedown positioning disk " direction, turn, this reduces making a concerted effort and being unloaded in its locomotive function by actuator 14 thus on " opening positioning disk " direction.When abutting on front side of positioning disk on shrouding disc 9 and no longer have volume flowrate flowing, positioning disk 12 is closed.The aperture of positioning disk 12 is the marks of the volume flowrate flowing through cooling medium pump.The number of the opening 11 offered in positioning disk 12, the aperture of positioning disk 12 can be found out and act on the association between the fluid force on positioning disk 12 from the figure of Fig. 4.Along with the increase of opening 11 number, when the aperture of positioning disk 12 is identical, force curve declines.But from the aperture determined, force curve partly rotates back into negative.This causes the masterpiece on " closedown positioning disk " direction to be used for positioning disk 12, therefore needs one " failure safe solution ".This means, as long as also need the cooling of motor, just mustn't by mistake close positioning disk 12.Use additional spring 8 to this solution.This spring to be encased in regulation unit 3 and to act on push rod 2b.This spring 8 must have pre-tensioner, even if thus when actuator 14 lost efficacy positioning disk 12 also get back to initial position through push rod 2b at the direction top offset of impeller 4.In order to again eliminate this negative force by so-called " failsafe springs ", must around the total force curve of the pre-tensioner raising of this spring 8.This power resulting through again opening 11 realization reduces partly loses again.That this causes using powerful and therefore occupy the actuator 14 of larger structure space.
As improvement project according to the present invention, therefore the opening 11 depending on the variable break-make of aperture of positioning disk 12 is proposed.This realizes by closing profile 5, and closedown profile 5 is loaded into and is provided with in the impeller 4 of blade 6.As shown in Figure 2 to Figure 3, in this steel embedded piece that can be encased in impeller 4 or in extruding encapsulating of impeller or also can in the blade of impeller itself.By making positioning disk 12 move axially on the direction of impeller 4, the closing element 5a formed in foliaceous to be engaged in one or more opening corresponding with it 11 and to close this opening 11.Utopian force curve 20 shown in figure in the diagram.Utopian force curve 20 indicates and almost keeps identical power effect to positioning disk 12, does not rely on its aperture.This Utopian force curve 20 only has when reaching the operation point S marked separately
xafter be just converted when "jump" to the operation point of settling recently.This is realized by the number of opening 11 and the aperture of positioning disk 12 changing positioning disk 12.
This is changed by stepless the opening of the opening 11 of positioning disk 12, so that " soft " of realizable force level, stable, non-change suddenly.The quality of non-adjustment suddenly to the control/adjustment of positioning disk position plays positive role, because can not there is unexpected power spring and the spring of position therefore.Number based on the opening 11 of closing in the geometrical shape of profile 5 and positioning disk 12 can realize this open-minded without bouncing
So infinitely open opening 11 to be realized by the particular design of closing element 5a.Allow the conical by its shape being not only closing element of this point, and be the foliaceous shape that it highly raises.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.The positioning disk 12 of deformation based and aperture is changed, and also make the opening 11 of partly or fully opening or closing different number owing to closing profile 5.Fig. 2 b and Fig. 2 d illustrates in the open position with the positioning disk 12 of the opening 11 of closing.This corresponds in the drawings from 100% aperture until the operating range of operation point S1.When positioning disk 12 is further at " closedown " direction top offset, opening 11 due to highly raise closing element 5a and by infinitely open-minded.Therefore more openings are little by little opened.This corresponds in the drawings between the S1 to S2 of operation point and also has the operating range between the S2 to S3 of operation point.Fig. 2 a and Fig. 2 c show with the opening 11 of not closing, in off position under positioning disk 12.This corresponds to the operating range between operation point S3 to S4 or 0% aperture in the drawings according to 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
S4 operation point 4
Claims (7)
1. the cooling medium pump for the cooling circuit of internal-combustion engine, described cooling medium pump has pump case (1), drivable axle (2a) is had at described pump case (1) internal support, impeller (4) at an end winding support of described axle (2a), described impeller (4) has the blade (6) charged in suction chamber (7) and is connected with shrouding disc (9), wherein, rotated together with described shrouding disc (9) by described impeller (4), fluid can be inhaled in described suction chamber (7) through the suction pipe joint of described pump case (1) (10) and also can be transported in described pump case (1) through described blade (6), wherein, arranging between described impeller (4) and described shrouding disc (9) can by the positioning disk (12) of regulation unit (3) axial displacement, described positioning disk (12) has the profile corresponding with described impeller (4) and the overhang (13) towards described impeller (4), it is characterized in that, described positioning disk (12) has at least one opening (11), described impeller (4) has closedown profile (5), and described closedown profile (5) points to described positioning disk (12), described closedown profile (5) can be engaged with one of opening of described positioning disk (12) (11) and partly or entirely close this opening.
2. cooling medium pump according to claim 1, is characterized in that, described closedown profile (5) has more than one closing element (5a), and wherein, the size of described each closing element (5a) can be different from each other.
3. cooling medium pump according to claim 2, is characterized in that, described closing element (5a) is implemented in foliaceous.
4. cooling medium pump according to claim 2, is characterized in that, described closing element (5a) is implemented taperedly.
5. the cooling medium pump according to claim 3 or 4, is characterized in that, described closedown profile (5) achieves the stepless closedown of described opening (11).
6. 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.
7. cooling medium pump according to claim 1, is characterized in that, described regulation unit (3) has spring (8), and described positioning disk (12) is got back to initial position by described spring (8) by adjustment.
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 CN103597212A (en) | 2014-02-19 |
| CN103597212B true 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 | Variable flow machine |
| 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 CN CN201280026098.7A patent/CN103597212B/en not_active Expired - Fee Related
- 2012-03-15 US US14/004,803 patent/US20140003913A1/en not_active Abandoned
- 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 | Variable flow machine |
| 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 |
|---|---|
| CN103597212A (en) | 2014-02-19 |
| US20140003913A1 (en) | 2014-01-02 |
| WO2012167961A1 (en) | 2012-12-13 |
| DE102011077029A1 (en) | 2012-12-13 |
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Address after: German Herzogenaurach Applicant after: SCHAEFFLER TECHNOLOGIES GmbH & Co.KG Address before: German Herzogenaurach Applicant before: Fifth Schaeffler investment management GmbH & Co.KG Address after: German Herzogenaurach Applicant after: SCHAEFFLER TECHNOLOGIES AG & CO.KG Address before: German Herzogenaurach Applicant before: SCHAEFFLER TECHNOLOGIES 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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| TA01 | Transfer of patent application right |
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| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20160330 Termination date: 20170315 |