WO2011018259A1 - Hochdruckpumpe - Google Patents
Hochdruckpumpe Download PDFInfo
- Publication number
- WO2011018259A1 WO2011018259A1 PCT/EP2010/058717 EP2010058717W WO2011018259A1 WO 2011018259 A1 WO2011018259 A1 WO 2011018259A1 EP 2010058717 W EP2010058717 W EP 2010058717W WO 2011018259 A1 WO2011018259 A1 WO 2011018259A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- roller
- pressure pump
- cover
- shoe
- roller shoe
- Prior art date
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
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
- F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/02—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type
- F02M59/10—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps of reciprocating-piston or reciprocating-cylinder type characterised by the piston-drive
- F02M59/102—Mechanical drive, e.g. tappets or cams
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
- F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
-
- 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
- F04B1/00—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders
- F04B1/04—Multi-cylinder machines or pumps characterised by number or arrangement of cylinders having cylinders in star- or fan-arrangement
- F04B1/0404—Details or component parts
- F04B1/0439—Supporting or guiding means for the pistons
-
- 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
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/02—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical
- F04B9/04—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms
- F04B9/042—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being mechanical the means being cams, eccentrics or pin-and-slot mechanisms the means being cams
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
- F02M2200/8023—Fuel injection apparatus manufacture, repair or assembly the assembly involving use of quick-acting mechanisms, e.g. clips
Definitions
- the invention relates to a high pressure pump for a fuel injection device of an internal combustion engine with the features of the preamble of claim 1.
- a high pressure pump is for example from the document DE 10th
- the high pressure pump described herein includes a drive shaft having at least one cam or eccentric and at least one pumping element including a pump piston which is driven in a reciprocating motion by the cam or eccentric of the drive shaft.
- a pump piston which is driven in a reciprocating motion by the cam or eccentric of the drive shaft.
- Zwi see the pump piston and the cam or eccentric of the drive shaft, a support member and a rolling on the cam or eccentric roller are arranged.
- the support member has on its side facing the drive shaft a recess in which the roller is rotatably mounted.
- a plunger assembly which has a bearing element for partially receiving a roller, wherein the Lagerele- ment is formed free of captive holding the roller, that is, that the bearing element, the role over an angular range ⁇ 180 ° wraps around.
- the plunger assembly therefore also has a cap with retaining lugs, which - viewed in cross section - engage behind the role.
- the semi-cylindrical cavity of the bearing element adapted to the roll has a larger radius than the roll.
- the bearing element lies against the roller only in a partial region, that is, the contact region is further reduced.
- radial gaps which is the entry of
- Object of the present invention is to provide a high-pressure pump of the type mentioned, which has at least one pump element which comprises an improved support of the pump piston on the cam or eccentric drive shaft via a plunger and a roller.
- the roller should be mounted as low as possible in the ram or an additional support element used therein.
- the proposed high-pressure pump has at least one pump element with a pump piston, which can be driven by a cam or eccentric drive shaft in a reciprocating motion, wherein the pump piston indirectly via a plunger body and a roller on the cam or eccentric of the drive shaft is supported.
- a roller shoe is provided with a substantially partially cylindrical recess for partially accommodating the roller in the tappet body.
- the substantially part-cylindrical recess of the roller shoe forms longitudinal edges with an end face of the roller shoe, which are rounded or beveled for receiving a coating which extends from the recess over the longitudinal edges. The coating essentially lines the recess of the roller shoe and is thereby guided beyond the longitudinal edges.
- the proposed edge formation ensures that improved adhesion of the coating in the area of the longitudinal edges is ensured. is done. This in turn causes the wear in the region of the longitudinal edges, for example due to a faulty coating, can be significantly reduced.
- the coating serves to form a sliding layer and / or a wear layer and is preferably made of carbon or a carbon compound. Since the roller shoe is used, in particular, for supporting the roller running on the cam or on the eccentric of the drive shaft, the recess can be formed into the slide bearing by means of a suitably formed coating. Coatings of carbon or carbon compounds have proved particularly advantageous in this context. In addition, if a coating is chosen which has a high wear resistance, the wear in the contact area between the roller shoe and the roller can be further reduced.
- At least one rounded or chamfered longitudinal edge has a radial distance to the roller.
- the cross-sectional profile of the essentially part-cylindrical recess of the roller shoe thus deviates from the cross-sectional profile of the roller at least in a partial region.
- the part-cylindrical recess may have a larger diameter in cross-section than the roller.
- the part-cylindrical recess can follow the profile of an ellipse in cross section, which widens toward the longitudinal edges.
- the radial distance of a longitudinal edge to the roller causes a relief of the longitudinal edge, so that this measure also contributes to a reduction of wear on the roller shoe and the role.
- a radial gap between the roller shoe and the roller entails the risk of dirt particles being introduced into the gap between the roller shoe and the roller, which could injure the coating formed inside the recess.
- the roller shoe has a cover which extends at least over a partial area of the end face and over at least one longitudinal edge in such a way that an edge running parallel to the longitudinal axis A of the roller is formed has a small game to the role. Accordingly, the radial gap can be protected from penetrating dirt particles by the cover of the roller shoe, so that further low wear in the contact area between roller shoe and roller is ensured.
- the cover is preferably arranged on both sides of the roller. If only one longitudinal edge and its radial gap to the roll are protected by a corresponding cover, the cover is preferably arranged on the direction of rotation side, since the entry of
- the edge of the cover which is guided parallel to the longitudinal axis A of the roller, preferably extends over the entire length of the longitudinal edge which it covers. That is, the axial extent of the edge of the cover is at least equal to the axial extent of the covered longitudinal edge of the recess. In this way it can be ensured that over the entire axial extension of the radial gap between longitudinal edge and roller penetrating dirt particles are successfully rejected.
- the edge of the cover which is spaced apart from the roller by a small amount of play, is designed to run obliquely and / or concavely rounded.
- the acute-angled and thus preferably sharp-edged design of the edge with a small radial clearance to the roller edge causes the cover assumes the function of a dirt wiper.
- the cover is connected to the roller shoe via a screw, clamp or latching connection. This ensures a secure hold of the cover on the roller shoe.
- a particularly simple assembly allow clamping or latching connections, which thereby realizes can be siert that arranged on the cover locking elements are inserted into corresponding recesses on the roller shoe.
- a secure mounting of the cover on the roller shoe is particularly important if the cover in addition to the function as dirt deflector or
- Dirt wiper also assumes a holding function. This is the case when only the cover of the role - viewed in cross-section - engages behind, so that only the cover ensures a captive holding the role in the roller shoe.
- the invention also includes embodiments in which the recess of the roller shoe has a cross-sectional profile which engages behind the roller. This means that the wrap angle can also be> 180 °.
- the cover of the roller shoe is designed in several parts, preferably the cover consists of two parts, each part of which is guided parallel to the longitudinal axis A of the roller
- a two-part embodiment of the cover has the advantage that the insertion of the roller is facilitated in the roller shoe, since in particular a designed for captive holding the roller cover must be designed such that it engages behind the roller.
- roller shoe and the plunger body may also be integrally formed.
- the present invention is characterized in particular by a robust coating for improving the sliding and / or wear properties of the roller bearing in the roller shoe and thus by a lower wear in the contact area of the roller with the roller shoe. In addition, the function of dirt repellency is retained.
- FIG. 1 shows a schematic longitudinal section through a pump element of a high-pressure pump according to the invention in the region of the roller bearing, wherein the left half represents a first embodiment and the right half represents a second embodiment, and
- the pump element comprises a pump piston 1 which is supported via a roller 4 on a cam 2 of a drive shaft (not shown), so that the rotational movement of the drive shaft or of the cam 2 is transferred into a stroke movement of the piston 1.
- the roller 4 thereby runs on the outer peripheral surface of the cam 2, wherein it moves realtiv to a roller shoe 5, in which the roller 4 is partially received.
- the roller shoe 5 is in turn held in a plunger body 3 of the pump element.
- the roller shoe 5 has a substantially part-cylindrical recess 6, the cross-sectional profile of which is adapted to the cross-sectional profile of the roller 4 at least in a partial region. At least in this sub-area there is a contact between the roller shoe 5 and the roller 4, so that during operation of the pump this portion is dynamically stressed.
- the training 6 is lined with a coating 9, which serves to form a sliding bearing for the roller 4.
- the configuration of the recess 6 as a slide bearing causes the wear in the contact region of the recess 6 is reduced with the roller 4 by reducing the friction forces.
- the illustrated embodiments left half and right half of Fig.
- the recess 6 in cross section has a larger diameter than the roller 4, so that the contact area is limited to a portion of the recess 6, whereby the wear on the roller shoe 5 and / or the role 4 can be further reduced.
- the recess 6 on both sides of the roller 4 has a radial gap, which in the region of the longitudinal edges 7, which forms the recess 6 with an end face 8 of the roller shoe 5, each has its greatest radial extent.
- the radial gap relieves on the one hand the longitudinal edges 7, on the other hand it allows the entry of Dirt particles that could cause a violation of the coating 9 within the recess 6.
- a cover 10 is provided on the end face 8 of the roller shoe 5, which has a recess for the roller 4.
- edges 11 are formed, which have a slight radial clearance to the roller 4.
- the longitudinal edges 7 and the radial gap between the recess 6 and the roller 4 are covered as much as possible. Due to the small radial clearance of the cover 10 to the roller 4, a dirt entry is effectively prevented.
- the edges 1 1 of the cover 10 are sharp-edged, so that the cover 10 also has the function of a dirt wiper.
- the cover 10 also has the task to keep the role 4 captive in the recess 6 of the roller shoe 5. Because the roller shoe 5 is not able to do so, since the cross section of the recess 6 is formed such that the roller shoe 5, the roller 4 does not engage behind.
- the cover 10 in turn is connected by screws 13 with the roller shoe 5.
- An essential measure for the protection of the coating 9 within the recess 6 represents the inventive design of the longitudinal edges 7 of the recess 6 in the region of the intersection with the end face 8. According to the first embodiment shown in the left half of Figure 1 is the
- Longitudinal edge 7 formed beveled.
- the inclined surface of the chamfer mediates between the recess 6 and the end face 8, so that the formation of sharp edges is avoided. Because the chamfer encloses with the adjoining surfaces in each case an angle of significantly more than 90 °.
- the proposed embodiment of the longitudinal edge 7 thus causes improved adhesion
- FIG. 1 An alternative embodiment is shown in the right-hand holder of Figure 1. This differs from that of the left half in that the longitudinal edge 7 is rounded.
- the rounding has a radius Ri, which is chosen such that no burrs are formed.
- the cover 10 can also be held on the roller shoe 5 via a clamping or latching connection.
- the screws 13 can then be omitted.
- the clamping or latching connection is formed by a latching lug 14 on a side upstand of the cover 10 and a receiving groove 15 formed corresponding to the latching lug 14 in a side surface of the roller shoe 5.
- different variants of clamping or locking connections are possible.
- the cover 10 may also be connected to the plunger body 3.
- Fig. 2 also illustrates two embodiments.
- the left half of Figure 2 shows a first embodiment of the edge 1 1 of the cover 10, which is concavely rounded and with an outer surface 12 of the cover 10 encloses an acute angle.
- the rounding follows a radius R 2 .
- the right-hand side of FIG. 2 shows a second embodiment of the edge 11 of the cover 10, which, in contrast to the embodiment of the left-hand half, has an oblique design.
- the edge 1 1 encloses with the outer surface 12 of the cover 10 an acute angle ⁇ , which in the present case is 45 °.
- the function of the scraper is thus retained.
- the various exemplary embodiments of the longitudinal edges 7 and the edges 11 shown in FIGS. 1 and 2 can be combined as desired. In that regard, the specific training can be adapted to the respective requirements and / or the materials used in each case.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Fuel-Injection Apparatus (AREA)
- Sealing Devices (AREA)
- Details Of Reciprocating Pumps (AREA)
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
CN201080035244.3A CN102472218B (zh) | 2009-08-10 | 2010-06-21 | 高压泵 |
JP2012524164A JP5302465B2 (ja) | 2009-08-10 | 2010-06-21 | 高圧ポンプ |
KR1020127003485A KR101712688B1 (ko) | 2009-08-10 | 2010-06-21 | 고압 펌프 |
EP10728166.9A EP2464851B1 (de) | 2009-08-10 | 2010-06-21 | Hochdruckpumpe |
RU2012108433/06A RU2541485C2 (ru) | 2009-08-10 | 2010-06-21 | Насос высокого давления |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102009028378.1 | 2009-08-10 | ||
DE200910028378 DE102009028378A1 (de) | 2009-08-10 | 2009-08-10 | Hochdruckpumpe |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011018259A1 true WO2011018259A1 (de) | 2011-02-17 |
Family
ID=42647486
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2010/058717 WO2011018259A1 (de) | 2009-08-10 | 2010-06-21 | Hochdruckpumpe |
Country Status (7)
Country | Link |
---|---|
EP (1) | EP2464851B1 (de) |
JP (1) | JP5302465B2 (de) |
KR (1) | KR101712688B1 (de) |
CN (1) | CN102472218B (de) |
DE (1) | DE102009028378A1 (de) |
RU (1) | RU2541485C2 (de) |
WO (1) | WO2011018259A1 (de) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10436164B2 (en) * | 2014-12-23 | 2019-10-08 | Cummins, Inc. | Tappet roller retaining approach |
GB2593934A (en) * | 2020-04-10 | 2021-10-13 | Delphi Tech Ip Ltd | Drive assembly for a fuel pump |
Families Citing this family (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102011086703A1 (de) * | 2011-11-21 | 2013-05-23 | Robert Bosch Gmbh | Hochdruckpumpe |
DE102012201302A1 (de) * | 2012-01-31 | 2013-08-01 | Robert Bosch Gmbh | Hochdruckpumpe |
JP5895867B2 (ja) * | 2013-02-07 | 2016-03-30 | 株式会社デンソー | 燃料供給ポンプ |
JP5812020B2 (ja) * | 2013-02-07 | 2015-11-11 | 株式会社デンソー | 燃料供給ポンプ |
DE102014220746B3 (de) | 2014-10-14 | 2016-02-11 | Continental Automotive Gmbh | Kraftstoffpumpe |
DE102016219046A1 (de) * | 2016-09-30 | 2018-04-05 | Robert Bosch Gmbh | Stößelbaugruppe für eine Radialkolbenpumpe, Radialkolbenpumpe |
DE102017124274B3 (de) | 2017-10-18 | 2018-11-08 | Schaeffler Technologies AG & Co. KG | Gebauter Rollenstößel |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002295339A (ja) * | 2001-03-29 | 2002-10-09 | Denso Corp | 摺動部材およびこれを用いた燃料噴射ポンプ |
DE10326863A1 (de) * | 2003-06-14 | 2004-12-30 | Daimlerchrysler Ag | Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen |
WO2005031150A1 (de) * | 2003-09-26 | 2005-04-07 | Robert Bosch Gmbh | Stösselbaugruppe für eine hochdruckpumpe und hochdruckpumpe mit wenigstens einer stösselbaugruppe |
DE102005042598A1 (de) * | 2005-09-07 | 2007-03-22 | Ab Skf | Stößel |
DE102006041673A1 (de) * | 2006-02-20 | 2007-08-23 | Robert Bosch Gmbh | Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
RU2230213C2 (ru) * | 2002-08-19 | 2004-06-10 | ОАО Ярославский завод дизельной аппаратуры | Топливный насос высокого давления автомобильного дизеля |
EP1582735A4 (de) * | 2003-01-09 | 2006-06-07 | Bosch Automotive Systems Corp | Kraftstoffzufuhrpumpe |
JP2004324535A (ja) * | 2003-04-24 | 2004-11-18 | Bosch Automotive Systems Corp | 燃料供給用ポンプおよびタペット構造体 |
DE10326880A1 (de) * | 2003-06-14 | 2004-12-30 | Daimlerchrysler Ag | Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen |
DE10355028A1 (de) * | 2003-11-25 | 2005-06-23 | Robert Bosch Gmbh | Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine |
US7497157B2 (en) * | 2004-01-14 | 2009-03-03 | Bosch Corporation | Fuel supply pump and tappet structural body |
JP4467469B2 (ja) * | 2005-06-08 | 2010-05-26 | ボッシュ株式会社 | 燃料供給用ポンプ及びタペット構造体 |
RU2299351C1 (ru) * | 2005-11-21 | 2007-05-20 | Рязанский военный автомобильный институт им. ген. армии В.П. Дубынина | Способ определения угла начала нагнетания топлива секцией топливного насоса высокого давления |
-
2009
- 2009-08-10 DE DE200910028378 patent/DE102009028378A1/de not_active Withdrawn
-
2010
- 2010-06-21 WO PCT/EP2010/058717 patent/WO2011018259A1/de active Application Filing
- 2010-06-21 CN CN201080035244.3A patent/CN102472218B/zh not_active Expired - Fee Related
- 2010-06-21 RU RU2012108433/06A patent/RU2541485C2/ru not_active IP Right Cessation
- 2010-06-21 JP JP2012524164A patent/JP5302465B2/ja not_active Expired - Fee Related
- 2010-06-21 EP EP10728166.9A patent/EP2464851B1/de not_active Not-in-force
- 2010-06-21 KR KR1020127003485A patent/KR101712688B1/ko active IP Right Grant
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2002295339A (ja) * | 2001-03-29 | 2002-10-09 | Denso Corp | 摺動部材およびこれを用いた燃料噴射ポンプ |
DE10326863A1 (de) * | 2003-06-14 | 2004-12-30 | Daimlerchrysler Ag | Radialkolbenpumpe zur Kraftstoffhochdruckerzeugung bei Kraftstoffeinspritzsystemen von Brennkraftmaschinen |
WO2005031150A1 (de) * | 2003-09-26 | 2005-04-07 | Robert Bosch Gmbh | Stösselbaugruppe für eine hochdruckpumpe und hochdruckpumpe mit wenigstens einer stösselbaugruppe |
DE102005042598A1 (de) * | 2005-09-07 | 2007-03-22 | Ab Skf | Stößel |
DE102006041673A1 (de) * | 2006-02-20 | 2007-08-23 | Robert Bosch Gmbh | Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US10436164B2 (en) * | 2014-12-23 | 2019-10-08 | Cummins, Inc. | Tappet roller retaining approach |
GB2593934A (en) * | 2020-04-10 | 2021-10-13 | Delphi Tech Ip Ltd | Drive assembly for a fuel pump |
GB2593934B (en) * | 2020-04-10 | 2022-08-03 | Delphi Tech Ip Ltd | Drive assembly for a fuel pump |
Also Published As
Publication number | Publication date |
---|---|
EP2464851B1 (de) | 2013-09-11 |
JP5302465B2 (ja) | 2013-10-02 |
JP2013501875A (ja) | 2013-01-17 |
EP2464851A1 (de) | 2012-06-20 |
DE102009028378A1 (de) | 2011-02-17 |
KR101712688B1 (ko) | 2017-03-22 |
RU2541485C2 (ru) | 2015-02-20 |
RU2012108433A (ru) | 2013-10-20 |
CN102472218B (zh) | 2014-11-26 |
CN102472218A (zh) | 2012-05-23 |
KR20120052294A (ko) | 2012-05-23 |
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