WO2012127980A1 - 流体圧シリンダのピストン軸受け構造 - Google Patents
流体圧シリンダのピストン軸受け構造 Download PDFInfo
- Publication number
- WO2012127980A1 WO2012127980A1 PCT/JP2012/054576 JP2012054576W WO2012127980A1 WO 2012127980 A1 WO2012127980 A1 WO 2012127980A1 JP 2012054576 W JP2012054576 W JP 2012054576W WO 2012127980 A1 WO2012127980 A1 WO 2012127980A1
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- WIPO (PCT)
- Prior art keywords
- backup
- ring
- groove
- piston
- wear ring
- Prior art date
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/166—Sealings between relatively-moving surfaces with means to prevent the extrusion of the packing
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/08—Characterised by the construction of the motor unit
- F15B15/14—Characterised by the construction of the motor unit of the straight-cylinder type
- F15B15/1423—Component parts; Constructional details
- F15B15/1447—Pistons; Piston to piston rod assemblies
- F15B15/1452—Piston sealings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/18—Sealings between relatively-moving surfaces with stuffing-boxes for elastic or plastic packings
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16J—PISTONS; CYLINDERS; SEALINGS
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
Definitions
- the present invention relates to a piston bearing structure of a fluid pressure cylinder in which a piston is supported by a cylinder tube.
- a piston bearing structure of a fluid pressure cylinder there is one in which a piston is supported by a cylinder tube via one seal ring and two wear rings sandwiching the seal ring.
- JP2010-14201A and JP2008-138805A disclose a seal ring having an X-shaped cross-sectional shape having two pairs of lips protruding on the inner and outer circumferences.
- this type of wear ring performs a backup function for supporting the seal ring lip so as not to protrude from the housing groove, and a bearing function for supporting the piston slidably with respect to the cylinder tube.
- a gap is defined around the wear ring, so that a pressure difference between the piston and the cylinder tube and on both sides of the wear ring is suppressed. The deformation is prevented by the difference.
- a backup wear ring having an L-shaped cross-section having a backup ring portion that performs a backup function and a wear ring portion that performs a bearing function may be used.
- the wear ring part is provided with an abutment gap
- the backup ring part is bias-cut to make an abutment gap, so that the backup wear ring is located between the piston and the cylinder tube when the hydraulic cylinder is extended or contracted. It is conceivable to suppress the pressure difference between the two sides.
- the piston may be inclined with respect to the center axis of the cylinder tube.
- the mouth gap may be blocked.
- An object of the present invention is to provide a piston bearing structure for a fluid pressure cylinder that can prevent pressure accumulation even when a backup wear ring having an L-shaped cross-section is used.
- a piston bearing structure of a hydraulic cylinder in which a piston is supported by a cylinder tube, the seal ring being accommodated in the piston housing groove and slidably contacting the cylinder tube, and the housing groove
- Two backup wear rings that sandwich the seal ring and are in sliding contact with the cylinder tube, and the housing groove includes a deep groove that accommodates the seal ring, and two grooves that extend in connection with both sides of the deep groove.
- a backup wear ring having an L-shaped cross section having a wear ring portion that is received in the shallow groove and receives the load of the piston, and a backup ring portion that is received in the deep groove and faces the seal ring.
- the wear ring part has a pair of joint end parts forming a joint gap, and the backup ring part is a pair of abutting each other
- the backup wear ring has a pressure relief groove extending across the backup ring part and the wear ring part against the receiving groove, and the pressure relief groove is formed between the piston and the cylinder tube.
- a piston bearing structure of a fluid pressure cylinder communicating between both sides of a backup wear ring therebetween.
- FIG. 1 is a longitudinal sectional view of a fluid pressure cylinder showing an embodiment of the present invention.
- FIG. 2 is a longitudinal sectional view of a fluid pressure cylinder in which a part of FIG. 1 is enlarged.
- FIG. 3 is a perspective view of the backup wear ring.
- FIG. 4 is a side view of the backup wear ring.
- FIG. 5 is a side view of backup wear ring according to another embodiment.
- FIG. 6 is a side view of backup wear ring according to another embodiment.
- the fluid pressure cylinder 1 and 2 are longitudinal sectional views showing a part of a fluid pressure cylinder (hydraulic cylinder) 1.
- the fluid pressure cylinder 1 is used as an actuator that drives a load of, for example, a work machine, a construction machine, another machine, or a facility.
- the fluid pressure cylinder 1 uses oil as a working fluid.
- a working fluid liquid
- a water-soluble alternative liquid may be used.
- the fluid pressure cylinder 1 includes a cylindrical cylinder tube 2, a piston 3 slidably housed inside the cylinder tube 2, a piston rod 7 connected to the piston 3, and a piston rod 7 with respect to the cylinder tube 2.
- a cylinder head that slidably supports the cylinder head.
- the cylinder tube 2, piston rod 7, piston 3, and cylinder head are arranged coaxially with respect to the central axis P.
- the inside of the cylinder tube 2 is partitioned by a piston 3 into a fluid pressure chamber 5 on the rod side and a fluid pressure chamber 6 on the end side.
- the fluid pressure chamber 5 on the rod side and the fluid pressure chamber 6 on the end side communicate with the fluid pressure unit via a pipe.
- the single-acting fluid pressure cylinder 1 is extended by introducing a pressurized working fluid supplied from a fluid pressure unit into an end-side fluid pressure chamber 6, and the pressurized working fluid is moved to a rod-side fluid pressure chamber. By being introduced into 5, the contraction operation is performed.
- a backup wear ring (wear ring) 20, a seal ring 50, and a backup wear ring (wear ring) 20 are interposed between the outer periphery of the piston 3 and the inner peripheral surface 2i of the cylinder tube 2 in order from the top in FIG. .
- An accommodation groove 11 extending in an annular shape is formed on the outer peripheral surface 3 o of the piston 3, and each backup wear ring 20 and the seal ring 50 are accommodated in the accommodation groove 11.
- the housing groove 11 has one deep groove 13 and two shallow grooves 12 that extend in connection with both side portions of the deep groove 13.
- a seal ring 50 is accommodated in the central deep groove 13, and each backup wear ring 20 is accommodated across the deep groove 13 and the upper and lower shallow grooves 12.
- the shallow groove 12 and the deep groove 13 have an L-shaped cross-sectional shape in which two rectangles are combined.
- the bottom surface 12a of the shallow groove 12 and the bottom surface 13a of the deep groove 13 are each formed in a right cylindrical surface shape with the central axis P as the center.
- the side surface 12b of the shallow groove 12 and the both side surfaces 13b of the deep groove 13 are formed in a planar shape that is substantially orthogonal to the central axis P, respectively.
- the seal ring 50 has an X-shaped cross section and is formed in an annular shape.
- the seal ring 50 is formed in a substantially line-symmetric shape having two pairs of lips 51 and 52 projecting on the inner and outer peripheries.
- the seal ring 50 is formed of a resin material such as urethane rubber.
- the lip 51, 52 expands due to the elastic restoring force and fluid pressure, the inner lip 51 contacts the bottom surface 13a of the deep groove 13 over the entire circumference, and the outer lip 52 is entirely It slidably contacts the inner peripheral surface 2i of the cylinder tube 2 over the circumference.
- the seal ring 50 seals between the fluid pressure chamber 5 on the rod side and the fluid pressure chamber 6 on the end side.
- an O-ring having a substantially circular cross-sectional shape may be used as the seal ring 50.
- the backup wear ring 20 has an L-shaped cross section and is formed in an annular shape.
- the backup wear ring 20 includes a wear ring portion 21 that is accommodated in the shallow groove 12 and receives the load of the piston 3, and a backup ring portion 31 that is accommodated in the deep groove 13 and faces the seal ring 50.
- the backup wear ring 20 is formed of a resin material such as nylon, for example, and has higher rigidity than the seal ring 50.
- FIG. 3 is a perspective view of the backup wear ring 20.
- the wear ring part 21 is formed in a ring shape having a joint gap 22 defined by the joint end parts 21m and 21n.
- the backup wear ring 20 is fitted in the receiving groove 11 in a state where the opening gap 22 is widened.
- the wear ring portion 21 has a rectangular cross-sectional shape that is one side of an L shape, and has an inner peripheral surface 21i, an outer peripheral surface 21o, and a side surface 21j.
- the inner peripheral surface 21i and the outer peripheral surface 21o are each formed in a right cylindrical surface centered on the central axis P.
- the side surface 21j is formed in a planar shape that is substantially orthogonal to the central axis P.
- the joint end portions 21m and 21n of the wear ring portion 21 are formed in a planar shape facing each other.
- the backup wear ring 20 has an elastic restoring force that tries to open radially outward in the assembled state interposed in the cylinder tube 2, and the end portion of the mating end is caused by this elastic restoring force.
- 21 m and 21 n are separated from each other to define the opening gap 22.
- the wear ring portion 21 Since the wear ring portion 21 is formed with a thickness (diameter dimension) larger than a depth (diameter dimension) of the shallow groove 12, the outer peripheral surface 21o extends from the housing groove 11 in the outer diameter direction of the piston 3. It protrudes and the outer peripheral surface 21 o is in sliding contact with the inner peripheral surface 2 i of the cylinder tube 2. Thereby, the wear ring part 21 fulfill
- the backup ring portion 31 has a rectangular cross-sectional shape that is one side of an L-shape, and includes an inner peripheral surface 31i, an outer peripheral surface 31o, a back surface (side surface) 31j, and a backup surface (side surface) 31k.
- the inner peripheral surface 31 i and the outer peripheral surface 31 o are each formed in a right cylindrical surface centered on the central axis P.
- the outer peripheral surface 31o is continuous with the outer peripheral surface 21o of the wear ring portion 21 without a step.
- the back surface 31j and the backup surface 31k are formed in a planar shape that is substantially orthogonal to the central axis P.
- the backup wear ring 20 supports the lip 52 of the seal ring 50 pressed against the backup surface 31k so as not to protrude to the inner peripheral surface 2i side of the cylinder tube 2, and the lip 51 protrudes to the bottom surface 13a side of the deep groove 13.
- the backup function is supported so that there is no.
- the backup ring portion 31 has a pair of bias cut end portions 31m and 31n that come into contact with each other. Since the end faces 31m and 31n of the bias cut end are formed in a tapered shape whose end faces are inclined with respect to the central axis P, the end faces remain in contact with each other even when the backup wear ring 20 opens radially outward. It is held and there is no gap between them. Thereby, the backup ring part 31 fulfill
- the seal ring 50 is formed with an annular chamfered portion at the tip corners of the inner and outer peripheral lips 51 and 52.
- a chamfered portion 51 a is formed at the tip of the inner peripheral lip 51.
- the chamfering width T is a distance from the bottom surface 13 a of the deep groove 13 to the outer peripheral end of the chamfered portion 51 a in a state where the seal ring 50 is interposed in the housing groove 11.
- the chamfering width T is arbitrarily set.
- the backup wear ring 20 is configured such that the outer peripheral surface 31 o of the backup ring portion 31 is in contact with the inner peripheral surface 2 i of the cylinder tube 2 and the inner peripheral surface 31 i of the backup ring portion 31 and the deep groove 13 A gap of the clearance S is provided between the bottom surface 13a.
- the backup wear ring 20 has its outer peripheral surfaces 21 o and 31 o slidably contact the inner peripheral surface 2 i of the cylinder tube 2 by its elastic restoring force, and the inner peripheral surfaces 21 i and 31 i are the bottom surfaces of the shallow grooves 12. 12a, away from the bottom surface 13a of the deep groove 13.
- the working fluid can pass through the gaps defined between the inner peripheral surfaces 21i and 31i and the bottom surface 12a of the shallow groove 12 and the bottom surface 13a of the deep groove 13, so that the backup wear ring 20 and the seal ring 50 The working fluid is not confined during this period.
- the piston 3 is inclined with respect to the central axis P, so that the outer peripheral portion of the backup ring portion 31 is in sliding contact with the inner peripheral surface 2i of the cylinder tube 2 over the entire circumference.
- the back surface 31j of the backup ring portion 31 contacts the side surface 13b of the deep groove 13 over the entire circumference. As a result, the gap between the bias cut end portions 31m and 31n may be closed.
- the pressure relief groove 40 is formed in the backup wear ring 20.
- the pressure relief groove 40 communicates both sides of the backup wear ring 20 between the piston 3 and the cylinder tube 2.
- the pressure relief groove 40 extends from the inner peripheral surface 31 i of the backup ring portion 31 to the rear surface 31 j and the inner peripheral surface 21 i of the wear ring portion 21 so as to bend and extend to the side surface 21 j. Formed.
- the pressure relief groove 40 has one end 40 a that opens to the backup surface 31 k of the backup ring portion 31, and the other end 40 b that opens to the outer peripheral surface 21 o of the wear ring portion 21.
- the pressure relief groove 40 has a substantially semicircular cross-sectional shape as shown in FIG.
- the opening width of the gap provided between the inner peripheral surface 31 i of the backup ring portion 31 and the bottom surface 13 a of the deep groove 13 is defined as the inner peripheral clearance S of the backup ring portion 31. If the distance from the chamfered portion 51a of the lip 51 of the seal ring 50 to the outer peripheral end of the chamfered portion 13a is the chamfer width T, the depth U of the pressure relief groove 40 is set to satisfy the following equation. U + S ⁇ T (1) U ⁇ TS
- the depth U of the pressure relief groove 40 is set to be smaller than the difference between the chamfering width T and the inner circumferential clearance S of the backup ring portion 31.
- the lip 51 faces so that a part of the chamfered portion 51 a covers the opening of the pressure relief groove 40, and a part of the lip 51 can be prevented from protruding into the pressure relief groove 40.
- Each pressure relief groove 40 is formed at a position having an angle of about 90 degrees with respect to the abutment gap 22 around the central axis P.
- one pressure relief groove 40 may be formed in the backup wear ring 20.
- the pressure relief groove 40 is formed at a position having an angle of about 180 degrees with respect to the abutment gap 22 around the central axis P.
- three or more pressure relief grooves 40 may be formed in the backup wear ring 20.
- the piston bearing structure of the fluid pressure cylinder 1 is configured as described above. Thereby, even in the operating state where the gap around the backup ring portion 31 is closed, the pressure relief groove 40 communicates between both sides of the backup wear ring 20 between the piston 3 and the cylinder tube 2. The working fluid is confined between the seal ring 50 and the pressure difference between the two sides of the backup wear ring 20 can be suppressed. Therefore, a part of the backup wear ring 20 is prevented from being deformed and protruding from the receiving groove 11, and the bearing function of the backup wear ring 20 can be maintained.
- the pressure relief groove 40 has a substantially semicircular cross-sectional shape.
- the pressure relief groove 40 may have a substantially triangular cross-sectional shape.
- the pressure relief groove 40 may have a substantially rectangular cross-sectional shape.
- the piston bearing structure of the fluid pressure cylinder 1 in which the piston 3 is supported by the cylinder tube 2 includes one seal ring 50 that is in sliding contact with the cylinder tube 2, and two backup wear rings 20 that sandwich the seal ring 50.
- the accommodation groove 11 includes a deep groove 13 that accommodates the seal ring 50 and two shallow grooves 12 that are connected to both side portions of the deep groove 13 and extend.
- the backup wear ring 20 is an L-shaped cross-section having a wear ring part 21 received in the shallow groove 12 and receiving the load of the piston 3, and a backup ring part 31 received in the deep groove 13 and facing the seal ring 50. have.
- the wear ring portion 21 has a pair of end portions 21m and 21n that form the end portion gap 22, and the backup ring portion 31 has a pair of bias cut end portions 31m and 31n that come into contact with each other.
- the backup wear ring 20 has a pressure relief groove 40 extending across the backup ring portion 31 and the wear ring portion 21 so as to face the accommodation groove 11.
- a pressure relief groove 40 communicates on both sides of the backup wear ring 20 between the piston 3 and the cylinder tube 2.
- the pressure relief groove 40 communicates on both sides of the backup wear ring 20 between the piston 3 and the cylinder tube 2. It is possible to prevent a part of 20 from being deformed and protruding from the accommodation groove 11, and to maintain the bearing function of the backup wear ring 20.
- the pressure relief groove 40 opens opposite to the housing groove 11 and does not have a portion that slides on the inner peripheral surface 2i of the cylinder tube 2, sludge or the like can be prevented from clogging the pressure relief groove 40, and the pressure relief groove 40 can be prevented.
- the communication state of can be maintained.
- the seal ring 50 has an X-shaped cross-sectional shape having two pairs of lips 51 and 52 projecting on the inner and outer circumferences, and the lip 51 projecting on the inner circumference contacts the bottom surface 13 a of the deep groove 13.
- An annular chamfer 51a is formed.
- the distance from the bottom surface 13a of the deep groove 13 to the outer peripheral end of the chamfered portion 51a is defined as the chamfering width T of the seal ring 50, and the opening width of the gap provided between the inner peripheral surface 31i of the backup ring portion 31 and the bottom surface 13a of the deep groove 13 Is the clearance S, the depth U of the pressure relief groove 40 is set to be smaller than the difference between the chamfering width T of the seal ring 50 and the inner circumferential clearance S of the backup ring portion 31.
- the lip 51 faces so that a part of the chamfered portion 51 a covers the opening of the pressure relief groove 40, so that a part of the lip 51 can be prevented from protruding into the pressure relief groove 40.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Sealing Devices (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
- Actuator (AREA)
- Sealing With Elastic Sealing Lips (AREA)
Abstract
Description
U+S<T …(1)
U<T-S
Claims (2)
- ピストンがシリンダチューブに支持される流体圧シリンダのピストン軸受け構造であって、
前記ピストンの収容溝に収容されて前記シリンダチューブに摺接する1本のシールリングと、
前記収容溝に収容されて前記シリンダチューブに摺接する、前記シールリングを挟持する2本のバックアップウェアリングと、
を備え、
前記収容溝は、前記シールリングを収容する深溝と、前記深溝の両側部に連接して延びる2本の浅溝と、を有し、
前記バックアップウェアリングは、前記浅溝に収容されて前記ピストンの荷重を受けるウェアリング部と、前記深溝に収容されて前記シールリングに対峙するバックアップリング部と、を有するL字形の断面形状を持ち、
前記ウェアリング部は合い口隙間を形成する一対の合い口端部を有し、
前記バックアップリング部は互いに当接する一対のバイアスカット合い口端部を有し、
前記バックアップウェアリングは前記収容溝に対峙して前記バックアップリング部と前記ウェアリング部とに渡って延びる圧力逃がし溝を有し、
前記圧力逃がし溝は、前記ピストンと前記シリンダチューブとの間における前記バックアップウェアリングの両側を連通する流体圧シリンダのピストン軸受け構造。 - 請求項1に記載の流体圧シリンダのピストン軸受構造であって、
前記シールリングはその内外周に突出する2対のリップを有するX字形の断面形状を持ち、
前記シールリングの内周に突出する前記リップには、前記深溝の底面に当接する環状の面取り部が形成され、
前記深溝の底面から前記面取り部の外周端までの距離を前記シールリングの面取り幅Tとし、前記バックアップリング部の内周面と前記深溝の底面との間に設けられる間隙の開口幅をスキマSとすると、前記圧力逃がし溝の深さUは、前記面取り幅TとスキマSとの差より小さい寸法に設定される流体圧シリンダのピストン軸受け構造。
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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KR1020137001636A KR101478926B1 (ko) | 2011-03-23 | 2012-02-24 | 유체압 실린더의 피스톤 베어링 구조 |
US13/809,491 US9388902B2 (en) | 2011-03-23 | 2012-02-24 | Piston bearing structure for fluid pressure cylinder |
CN201280002792.5A CN103097745B (zh) | 2011-03-23 | 2012-02-24 | 流体压缸的活塞轴承构造 |
Applications Claiming Priority (2)
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JP2011063703A JP5604345B2 (ja) | 2011-03-23 | 2011-03-23 | 流体圧シリンダのピストン軸受け構造 |
JP2011-063703 | 2011-03-23 |
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WO2012127980A1 true WO2012127980A1 (ja) | 2012-09-27 |
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PCT/JP2012/054576 WO2012127980A1 (ja) | 2011-03-23 | 2012-02-24 | 流体圧シリンダのピストン軸受け構造 |
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US (1) | US9388902B2 (ja) |
JP (1) | JP5604345B2 (ja) |
KR (1) | KR101478926B1 (ja) |
CN (1) | CN103097745B (ja) |
WO (1) | WO2012127980A1 (ja) |
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Also Published As
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KR101478926B1 (ko) | 2014-12-31 |
KR20130031350A (ko) | 2013-03-28 |
JP2012197908A (ja) | 2012-10-18 |
US9388902B2 (en) | 2016-07-12 |
CN103097745B (zh) | 2016-01-20 |
JP5604345B2 (ja) | 2014-10-08 |
US20130113165A1 (en) | 2013-05-09 |
CN103097745A (zh) | 2013-05-08 |
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