EP2464866B1 - Pompe à haute pression - Google Patents

Pompe à haute pression Download PDF

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Publication number
EP2464866B1
EP2464866B1 EP10740213.3A EP10740213A EP2464866B1 EP 2464866 B1 EP2464866 B1 EP 2464866B1 EP 10740213 A EP10740213 A EP 10740213A EP 2464866 B1 EP2464866 B1 EP 2464866B1
Authority
EP
European Patent Office
Prior art keywords
roller
pump
roller tappet
piston
tappet
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.)
Not-in-force
Application number
EP10740213.3A
Other languages
German (de)
English (en)
Other versions
EP2464866A1 (fr
Inventor
Arnold Gente
Matthias Greiner
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2464866A1 publication Critical patent/EP2464866A1/fr
Application granted granted Critical
Publication of EP2464866B1 publication Critical patent/EP2464866B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • 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

Definitions

  • the invention relates to a high-pressure pump, in particular a radial or linear piston pump. Specifically, the invention relates to the field of fuel pumps for fuel injection systems of air-compression, self-igniting internal combustion engines.
  • a high-pressure pump for a fuel injection device of an internal combustion engine has a pump housing, in which a pump element is arranged, which comprises a driven by a drive shaft in a stroke pump piston.
  • the pump piston is slidably guided in a cylinder bore of a part of the pump housing and limited in this one pump working space.
  • the pump piston is supported indirectly via a hollow cylindrical plunger on the drive shaft, wherein the plunger is slidably guided in a bore of a part of the pump housing in the direction of the longitudinal axis of the pump piston.
  • the known high pressure pump has the disadvantage that a certain height is required for the plunger body to ensure reliable guidance in the pump housing in the direction of the longitudinal axis of the pump piston. This affects the size of the high-pressure pump. Furthermore, further components are required, in particular a support element which is inserted in the ram in the drive shaft facing end portion to support the roller.
  • the pump piston is connected via a spring plate, on which a plunger spring is supported, with the plunger body.
  • the high pressure pump according to the invention with the features of claim 1 has the advantage that a compact design of the pump assembly is possible and thus the space required for the high-pressure pump space is reduced. Specifically, an embodiment of the pump assembly can be simplified.
  • the roller tappet in at least one support region, in which the roller tappet is supported radially in the bore of the housing part is configured to be bulbous.
  • the bulbous configuration can be achieved for example by grinding the roller tappet on its outside.
  • the roller tappet on the support area can be ground spherical. Due to the small lever arm between the axis of rotation of the roller and the support point of the roller tappet, a bending moment between the roller tappet and the pump piston with respect to the connection of the roller tappet with the pump piston, which takes place via the spring plate, be kept sufficiently small.
  • the roller tappet can be made relatively small, whereby the plunger spring designed weaker and also can be significantly reduced, since the plunger spring has less mass to carry with it.
  • This can also be a significant weight savings, that is, a reduction in the mass of the components of the pump assembly, can be achieved, for example, is 50%.
  • Reducing the plunger spring may also result in a reduction in the main dimension of a camshaft (drive shaft) to a cylinder head top. This advantage leads to further weight savings on the cylinder head and the pump housing. Based on the reduction and thus mass reduction of the roller tappet thus additional benefits.
  • the pump piston is designed substantially cylindrical. This can account for a piston foot on the pump piston.
  • the pump piston can be made from a rod material, with an optimally small diameter of the rod material being chosen to minimize a machining volume by turning and grinding.
  • the spring plate has at least one support extension which is guided along the main axis of the pump assembly laterally along the roller tappet and is on the roller beyond the roller tappet out, and that the support extension limits a side run of the roller along its axis of rotation.
  • the spring plate has two support extensions, which are guided on opposite sides along the main axis of the pump assembly laterally on the roller tappet and stand on the roller on the roller tappet out and that the support extensions on both sides limit a side run of the roller along its axis of rotation ,
  • the support extensions can be configured according to two ears or lobes that protect the pump housing from the side run of the role and keep the role in its desired position. The resulting forces from the roller start to the support extensions can be transferred to the pump piston.
  • the pump piston has a piston foot, which faces the roller tappet, and that the spring plate engages behind the piston foot of the pump piston for connecting the pump piston with the spring plate.
  • the pump piston is connected to the roller tappet, wherein the connection is effected by means of the spring plate.
  • the pump piston can be supported with its piston foot on the roller tappet.
  • the cam or a drive shaft, on which the cam is provided has at least one guide web associated with the cam, which limits a side run of the roller along its axis of rotation.
  • two such guide webs are provided, which bound both sides of a side run of the roller along its axis of rotation.
  • Such guide webs are preferably designed as circumferential and closed guide webs.
  • Such guide webs take over the function of a support extension of the spring plate or the like, so that simplifies the design of the pump assembly.
  • the roller can not rotate, as it is guided directly on a cam track of the cam.
  • Fig. 1 shows a high-pressure pump 1 in a partial, schematic, axial sectional view according to a first embodiment.
  • the high pressure pump 1 can be configured in particular as a radial or inline piston pump.
  • the high-pressure pump 1 is suitable as a fuel pump for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a preferred use of the high pressure pump 1 is for a fuel injection system having a fuel rail which stores diesel fuel under high pressure.
  • the high-pressure pump 1 according to the invention is also suitable for other applications.
  • the high-pressure pump 1 has a pump housing which comprises one or more housing parts 2.
  • a drive shaft 3 is arranged, which in the housing part 2 is stored.
  • the drive shaft 3 is rotatable about a rotation axis 4, wherein the drive can be effected by an internal combustion engine.
  • the drive shaft 3 has at least one cam 5.
  • the cam 5 can also be configured as a multiple cam. Further, the cam 5 may be formed by an eccentric portion of the drive shaft 3 or the like.
  • a pump assembly 6 is arranged, which is associated with the cam 5.
  • the pump assembly 6 has a main axis 7 which points at least approximately on the axis of rotation 4 of the drive shaft 3.
  • the pump assembly 6 is arranged at least substantially in a bore 8 of the housing part 2.
  • a cylinder head 9 is connected to the housing part 2.
  • a projection 10 of the cylinder head 9 protrudes into the bore 8.
  • the bore 8 is designed symmetrically with respect to the main axis 7.
  • the projection 10 of the cylinder head 9 is designed symmetrically with respect to the main axis 7.
  • the pump assembly 6 also has a pump piston 11 which is guided in a bore 12 of the projection 11 along the main axis 7.
  • the pump piston 11 defines a pump working space 13 in the bore 12.
  • fuel under a low pressure can flow into the pump working space 13 from a prefeed pump or the like when the pump piston 11 performs a suction stroke.
  • the high pressure fuel is delivered via an exhaust valve 15 to a fuel rail or the like.
  • a roller tappet 20 is also arranged, which receives a roller 21.
  • the roller tappet 20 is formed as a one-piece roller tappet part.
  • the roller 21 runs in operation on a cam surface 22 of the cam 5 from. As a result, a lifting movement caused by the cam 5 is transmitted via the roller 21 and the roller tappet 20 to the pump piston 11.
  • the pump assembly 6 has a spring plate 23 which is connected to the roller tappet 20.
  • the pump piston 11 is connected to the spring plate 23.
  • the pump piston 11 is pressed into the spring plate 23.
  • a plunger spring 24 is provided, which is supported on the one hand on the cylinder head 9 and on the other hand on the spring plate 23.
  • the spring plate 23 is acted upon by the force of the plunger spring 24, namely in the direction of a suction stroke of a pump piston 11.
  • the roller 21 always in contact with the cam surface 22 and in contact with the roller tappet 20 stands.
  • the pump piston 11 which is pressed into the spring plate 23, designed cylindrical.
  • the roller tappet 20 has on its outer side a support region 30.
  • the support region 30 of the roller tappet 20 is designed belly-shaped. This results in a bulbous support region 30 of the roller tappet 20, on which the roller tappet 20 comes into contact with the bore 8 in the radial direction with respect to the main axis 7.
  • the bulbous support portion 30 is configured so that a lever arm 31 between a rotation axis 32 of the roller 21 and a support point 33 between the bulbous support region (belly) 30 of the roller tappet 20 and the bore 8 of the housing part 2 is relatively small. Depending on the configuration, the lever arm 31 can also be negligibly small.
  • the roller tappet 20 is supported at the support point 33 on the bore 8, so that a transverse force occurs radially to the main axis 7 at the support point 33.
  • the roller tappet 20 is not prevented from tilting in the bore 8. This results in a certain torque introduction via the spring plate 23 on the pump piston 11. However, the torque generated is sufficiently small, so that a reliable operation is ensured.
  • the lateral force to be supported occurs as a force component of the roller force, which is introduced perpendicular to the main axis 7 of the cam drive.
  • the lateral force at normal cam pitches takes on a maximum of a quarter of the force applied by the cam force.
  • the piston actuation force acting on the Pump piston 11 acts in the direction of the main axis 7, is therefore significantly greater than the transverse force component.
  • the roller tappet 20 is guided in the bore 8, that the transverse force is introduced at least approximately at the height of the axis of rotation 32.
  • the lever arm 31 may be about 5 mm.
  • the tilting moment that occurs is smaller than the product of the force acting on the pump piston 11 in the direction of the main axis 7, the lever arm 31 of 5 mm and the tangent of 15 °.
  • the occurring tilting moment is smaller than the product of the forces acting on the pump piston 11 in the direction of the main axis 7 and 1.25 mm.
  • the strength of the pump piston 11 is sufficient even with a relatively small diameter of the pump piston 11 to accommodate the occurring tilting moment of the roller tappet 20.
  • the roller tappet 20 can be designed so that the point of force application does not move so far from the ideal point at the height of the axis of rotation 32 of the roller 21, that is, the lever arm 31 is relatively small.
  • the torque acting on the pump piston 11 can be further reduced by an offset of the bore 12 of the lug 10 to the rotation axis 4 of the drive shaft 3.
  • the main axis 7 of the pump assembly 6 is slightly past the axis of rotation 4 of the drive shaft 3.
  • Fig. 2 shows a partial representation of the in Fig. 1 shown high pressure pump 1 in a schematic sectional view along the section line designated II.
  • the spring plate 23 has in this embodiment support projections 35, 36 which laterally on the roller tappet 20 along the main axis 7 of the pump assembly 6 extend.
  • the support extensions 35, 36 are guided laterally on both sides of the roller tappet 20, wherein these are on the side of the roller 21 on the roller tappet 20 addition.
  • the support extension 35 has a stop surface 37.
  • the support extension 36 has a stop surface 38.
  • Fig. 3 shows a partial representation of the in Fig. 1 shown high pressure pump 1 along the designated III cutting line.
  • the roller tappet 20 has bores 39, 40, 41, 42, which also extend through the spring plate 23. About the holes 39 to 42, the bore 8 of the housing part 2 with an interior of the housing part 2, in which the drive shaft 3 is arranged, connected.
  • the bores 39 to 42 serve as compensation bores 39 to 42.
  • the compensation bores 39 to 42 serve to allow a flow of fuel. This avoids that takes place by the roller tappet 20, a compression of the fuel.
  • Fig. 4 shows a partial representation of the in Fig. 1 shown high-pressure pump 1 according to a second embodiment.
  • the Indian Fig. 4 shown excerpts section corresponds to that in the Fig. 2 shown illustration along the in Fig. 1 executed with II designated cutting line.
  • the pump piston 11 has a piston foot 50.
  • the piston base 50 has an end face 51, with which the pump piston 11 rests against the piston tappet 20 on its piston foot 50.
  • the spring plate 23 on a collar 25. With the collar 52 of the spring plate 23 engages behind the piston 50 of the pump piston 11 to connect the pump piston 11 with the spring plate 23 and thus also with the roller tappet 20.
  • the pump piston 11 is designed in this case tree-shaped.
  • the pump piston 11 can thus absorb tilting moments which act on the roller tappet 20.
  • the pump piston 11 On the piston foot 50, which faces the roller tappet 20, the pump piston 11 is made thicker than on a cylindrical part 53. This results in a high stability of the pump piston 11.
  • the spring plate 23 supporting extensions 35, 36. It is ensured by stop surfaces 37, 38 of the support extensions 35, 36, a two-sided limitation of the side run of the roller 21.
  • Fig. 5 shows the in the Fig. 1 shown high-pressure pump 1 in a partial representation according to a third embodiment.
  • guide webs 55, 56 are provided on the cam 5 or on the drive shaft 3, on which the cam 5 is provided.
  • the guide webs 55, 56 are in this case associated with the cam 5 and thus the pump assembly 6.
  • the guide webs 55, 56 are configured circumferentially.
  • the guide web 55 has a circumferential, inner guide surface 57.
  • the guide web 56 has a circumferential, inner guide surface 58.
  • the guide surfaces 57, 58 face each other.
  • the guide webs 55, 56 with the guide surfaces 57, 58 protrude in the radial direction beyond the cam surface 22 with respect to the rotation axis 4 of the drive shaft 3.
  • the guide surfaces 57, 58 of the guide webs 55, 56 thereby limit a possible side run of the roller 21 along the axis of rotation 32 of the roller 21.
  • Stützfort instruments 35, 36 as for example in the Fig. 2 and 4 are illustrated, can be omitted here.
  • the mass of the moving parts of the pump assembly 6, in particular the mass of the spring plate 23, can be further reduced. This allows a further optimization of the pump assembly 6.
  • a height of the roller tappet 20 in the direction of the main axis 7 can be optimized.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fuel-Injection Apparatus (AREA)

Claims (7)

  1. Pompe à haute pression (1), en particulier pompe à piston radial ou pompe à piston en ligne pour des installations d'injection de carburant de moteurs à combustion interne à auto-allumage et compression d'air, comprenant au moins un module de pompe (6) et un arbre d'entraînement (3) qui présente au moins une came (5) associée au module de pompe (6), le module de pompe (6) présentant un piston de pompe (11) guidé dans un alésage (12), un rouleau (21) roulant sur une surface de came (22) de la came (5) et un poussoir de rouleau (20) qui reçoit le rouleau (21), le piston de pompe (11) étant connecté au poussoir de rouleau (20) par le biais d'une coupelle de ressort (23) sur laquelle s'appuie un ressort de poussoir (24), et de ce fait un basculement du poussoir de rouleau (20) par rapport à un axe principal (7) du module de pompe (6) le long duquel le piston de pompe (11) peut être actionné étant limité,
    caractérisée en ce que
    le poussoir de rouleau (20) est supporté radialement dans un alésage (8) réalisé dans au moins une partie de boîtier (2) par rapport à l'axe principal (7) du module de pompe (6) et est configuré sous forme bombée dans au moins une région de support (30) dans laquelle le poussoir de rouleau (20) s'appuie radialement dans l'alésage (8) de la partie de boîtier (2), et en ce que le bombement (30) du poussoir de rouleau (20) dans la région de support est configuré de telle sorte qu'un bras de levier (31) entre l'axe de rotation (32) du rouleau (21) et un point d'appui (33) entre le bombement (30) du poussoir de rouleau (20) et l'alésage (8) de la partie de boîtier (2) mesure au maximum approximativement 5 mm.
  2. Pompe à haute pression selon la revendication 1,
    caractérisée en ce que
    le poussoir de rouleau (20) est formé au moins d'une partie de poussoir de rouleau (20), la partie de poussoir de rouleau (20) recevant le rouleau (21) et la partie de poussoir de rouleau (20) s'appuyant radialement par rapport à l'axe principal (7) du module de pompe (6) dans l'alésage (8) de la partie de boîtier (2).
  3. Pompe à haute pression selon la revendication 1 ou 2,
    caractérisée en ce que
    le piston de pompe (11) est enfoncé dans la coupelle de ressort (23).
  4. Pompe à haute pression selon l'une quelconque des revendications 1 à 3,
    caractérisée en ce que
    la coupelle de ressort (23) présente au moins une saillie de support (35, 36) qui est guidée latéralement le long du poussoir de rouleau (20) le long de l'axe principal (7) du module de pompe (6) et qui dépasse au niveau du rouleau (21) au-delà du poussoir de rouleau (20), et en ce que la saillie de support (35, 36) limite un roulement latéral du rouleau (21) le long de son axe de rotation (32).
  5. Pompe à haute pression selon l'une quelconque des revendications 1 à 4,
    caractérisée en ce que
    le piston de pompe (11) est configuré essentiellement sous forme cylindrique.
  6. Pompe à haute pression selon la revendication 1 ou 2,
    caractérisée en ce que
    le piston de pompe (11) présente une base de piston (50) qui est tournée vers le poussoir de rouleau (20), et en ce que la coupelle de ressort (23) vient en prise par l'arrière avec la base de piston (50) du piston de pompe (11) pour relier le piston de pompe (11) à la coupelle de ressort (23).
  7. Pompe à haute pression selon l'une quelconque des revendications 1 à 6,
    caractérisée en ce que
    la came (5) ou un arbre d'entraînement (3) sur lequel est prévue la came (5), présente au moins une nervure de guidage (55, 56) associée à la came (5), qui limite un roulement latéral du rouleau (21) le long de son axe de rotation (32).
EP10740213.3A 2009-08-10 2010-08-03 Pompe à haute pression Not-in-force EP2464866B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910028394 DE102009028394A1 (de) 2009-08-10 2009-08-10 Hochdruckpumpe
PCT/EP2010/061260 WO2011018389A1 (fr) 2009-08-10 2010-08-03 Pompe à haute pression

Publications (2)

Publication Number Publication Date
EP2464866A1 EP2464866A1 (fr) 2012-06-20
EP2464866B1 true EP2464866B1 (fr) 2016-10-12

Family

ID=43034340

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10740213.3A Not-in-force EP2464866B1 (fr) 2009-08-10 2010-08-03 Pompe à haute pression

Country Status (5)

Country Link
EP (1) EP2464866B1 (fr)
KR (1) KR101773210B1 (fr)
CN (1) CN102472258B (fr)
DE (1) DE102009028394A1 (fr)
WO (1) WO2011018389A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR101656089B1 (ko) * 2012-10-11 2016-09-08 콘티넨탈 오토모티브 게엠베하 롤러 태핏 조립체를 위한 다기능 롤러 클립
DE102013212302A1 (de) * 2013-06-26 2014-12-31 Robert Bosch Gmbh Hochdruckpumpe und Kraftstoffeinspritzanlage mit einer Hochdruckpumpe
DE102013218260A1 (de) 2013-09-12 2015-03-12 Continental Automotive Gmbh Rollenstößel
EP2915994A1 (fr) * 2014-03-06 2015-09-09 Continental Automotive GmbH Agencement de poussoir et pompe
CN104088769A (zh) * 2014-08-01 2014-10-08 吉首大学 偏心可调式柱塞泵
GB2543354A (en) 2015-10-16 2017-04-19 Gm Global Tech Operations Llc Roller tappet for a fuel unit pump of an internal combustion engine
DE102016203768B4 (de) * 2015-11-12 2017-10-26 Robert Bosch Gmbh Pumpe, insbesondere Hochdruckpumpe eines Kraftstoffeinspritzsystems, mit einem Montageverbund von Stößel-Baugruppe und Pumpenzylinderkopf, insbesondere durch eine Rastverbindung zwischen Federteller und Stößelkörper
GB2549303A (en) * 2016-04-12 2017-10-18 Delphi Int Operations Luxembourg Sarl High pressure fuel pump
CN107965434B (zh) * 2018-01-16 2019-04-09 上海交通大学 一种压缩膨胀机的驱动机构

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10355027A1 (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
DE102004002487A1 (de) * 2004-01-17 2005-08-11 Robert Bosch Gmbh Rollenstößel
DE102004004705A1 (de) * 2004-01-30 2005-08-18 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE102005046670A1 (de) 2005-09-29 2007-04-05 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE102006041673A1 (de) * 2006-02-20 2007-08-23 Robert Bosch Gmbh Hochdruckpumpe, insbesondere für eine Kraftstoffeinspritzeinrichtung einer Brennkraftmaschine
DE102006012458A1 (de) * 2006-03-17 2007-09-20 Robert Bosch Gmbh Rollenstößel für ein Pumpenelement einer Kraftstoffhochdruckpumpe
DE102006045933A1 (de) * 2006-09-28 2008-04-03 Robert Bosch Gmbh Stößelbaugruppe für eine Hochdruckpumpe und Hochdruckpumpe mit wenigstens einer Stößelbaugruppe
DE102006048722A1 (de) * 2006-10-16 2008-04-17 Robert Bosch Gmbh Kolbenpumpe, insbesondere Kraftstoffhochdruckpumpe, mit Rollenstößel
DE102008043436A1 (de) * 2008-11-04 2010-05-06 Robert Bosch Gmbh Kolbenpumpe mit einem Kolbenhalter
DE102009001096A1 (de) * 2009-02-24 2010-08-26 Robert Bosch Gmbh Radialkolbenpumpe mit einer Nockenwelle mit partiell gehärteten Nockenflanken

Also Published As

Publication number Publication date
CN102472258A (zh) 2012-05-23
WO2011018389A1 (fr) 2011-02-17
EP2464866A1 (fr) 2012-06-20
DE102009028394A1 (de) 2011-02-17
KR20120052293A (ko) 2012-05-23
CN102472258B (zh) 2015-08-12
KR101773210B1 (ko) 2017-08-31

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