CN103958947A - Hydraulic pressure booster cylinder - Google Patents

Hydraulic pressure booster cylinder Download PDF

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Publication number
CN103958947A
CN103958947A CN201280051849.0A CN201280051849A CN103958947A CN 103958947 A CN103958947 A CN 103958947A CN 201280051849 A CN201280051849 A CN 201280051849A CN 103958947 A CN103958947 A CN 103958947A
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CN
China
Prior art keywords
pneumatics
hydraulic
operating chamber
passage
chamber
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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.)
Pending
Application number
CN201280051849.0A
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Chinese (zh)
Inventor
朱多暎
朱宰硕
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Individual
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Individual
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Publication date
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Publication of CN103958947A publication Critical patent/CN103958947A/en
Pending legal-status Critical Current

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Classifications

    • 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
    • F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
    • 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
    • F16J10/00—Engine or like cylinders; Features of hollow, e.g. cylindrical, bodies in general
    • F16J10/02—Cylinders designed to receive moving pistons or plungers
    • 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
    • F16J1/00—Pistons; Trunk pistons; Plungers
    • F16J1/09—Pistons; Trunk pistons; Plungers with means for guiding fluids

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

Although a pressure is boosted only one time in a hydraulic pressure booster cylinder for controlling and pressure-boosting working fluid by using air pressure according to the related art, the present invention may solve the above-described limitation through the provision of a hydraulic pressure booster cylinder that continuously boosts pressure.

Description

Hydraulic type pressurized cylinder
Technical field
The present invention relates to a kind of hydraulic type pressurized cylinder, it has pneumatics control loop to move continuously as water pump makes the charged piston of hydraulic type pressurized cylinder.
Background technique
At present, pneumatics cylinder and hydro cylinder are used mainly for pressurization, wherein, are mainly used in binding clasp, extruder, trigger etc., and binding clasp or extruder demand motive power not when starting as mentioned above still, needs large driving force while finishing closing on.When therefore, pressurization need to close in the extruding of piston rod end with cylinder, produce larger driving force.
Due to demand as mentioned above, when determining the size of cylinder, while finishing in order to close in extruding, obtain the driving force that needs, can only use the cylinder that diameter is large and heavy.But while using the large and heavy cylinder of described diameter, action slows down slow relatively and operating efficiency reduces, and needs more pneumatics or the hydraulic oil of volume, therefore, power consumption is large and cost is high.
For solving described problem, following cylinder is disclosed, on the pipeline by cylinder sap pressure supply or pneumatics, connect pressure-increasing machine, and when the extruding of piston rod closes on end, apply higher pressure, thereby increase driving force when the extruding of piston rod closes on end.But, its complex structure of described cylinder, and need to possess four above solenoid valve, changeable pump and control gear etc., therefore, expensive and easily break down.
For solving the problem of existing cylinder, in No. 10-2004-0061763rd, Korea S's publication, No. 10-2005-0101646th, Korea S's publication, No. 10-2011-0070951st, Korea S's publication, No. 10-2011-0013097th, Korea S's publication, No. 10-2011-0071926th, Korea S's publication, No. 10-2005-0045086th, Korea S's publication etc., pressurized cylinder technology is disclosed.
But existing hydraulic type pressurized cylinder is the structure of a supercharging 1 time, therefore, for supercharging heavy wool amount more, need to increase diameter or the stroke of pressurized cylinder, for this reason, total length is elongated.
Summary of the invention
The present invention proposes for solving the problem of described existing hydraulic type pressurized cylinder, its object is, a kind of hydraulic type pressurized cylinder is provided, at charged piston formation main valve and the pneumatics control loop of hydraulic type pressurized cylinder, thereby, charged piston (taking out pump) to-and-fro motion continuously.
For reaching described object, the present invention is provided with action piston 2 towards the place ahead in body interior, by pneumatics operating chamber 15 supplies that retreat forwards of pneumatics path 10, retreat with pneumatics, by rearward pneumatics operating chamber 25 supplies of advancing of pneumatics passage 20, advance with pneumatics, rear at action piston 2 arranges separately oil pressure supercharging operating chamber 35 with the pneumatics operating chamber 25 of advancing of action piston 2, the charged piston 4 being supported by spring 11 acts on hydraulic operation chamber 45, described hydraulic operation chamber is communicated in hydraulic booster operating chamber 35 by the little boring 12 of bore, hydraulic type pressurized cylinder of the present invention comprises the piston 3 being supported by spring 11, the boring 12 that bore is little, the charged piston 4 of the inside of penetrating action piston 2, control the guiding valve 6 of charged piston 4, the non-return projection 5 that is supported and optionally contact with charged piston 4 by spring 33, pneumatics safety check 8, 9 and pneumatics loop (following, be called main valve).The hydraulic back-pressure valve 7 being supported by spring 22 is formed between hydraulic booster operating chamber 35 and hydraulic operation chamber 45, and when charged piston 4 retreats, described hydraulic back-pressure valve supplements hydraulic oil from hydraulic operation chamber 45 to hydraulic booster operating chamber 35.
The present invention is obviously short and with low cost compared to hydraulic type pressurized cylinder length, and it is little that space is set, existing hydraulic type pressurized cylinder be take maximum oil mass and is manufactured as benchmark, so energy consumption is many, but charged piston of the present invention is consistent and moves back and forth with oil mass, thereby there is energy-saving effect.
Accompanying drawing explanation
Fig. 1 is the longitudinal section of the structure of hydraulic type pressurized cylinder according to an embodiment of the invention.
The longitudinal section that described in when Fig. 2 is low-load, hydraulic type pressurized cylinder advances at utmost speed.
The longitudinal section that described in when Fig. 3 is high load, hydraulic type pressurized cylinder once advances.
Fig. 4 is the longitudinal section of front inlet side of the charged piston of described hydraulic type pressurized cylinder.
Fig. 5 is the longitudinal section that the charged piston of described hydraulic type pressurized cylinder retreats.
Fig. 6 is the longitudinal section that retreats end of the charged piston of described hydraulic type pressurized cylinder.
Fig. 7 is the longitudinal section that the secondary of the charged piston of described hydraulic type pressurized cylinder advances.
Fig. 8 is that the hydraulic oil of described hydraulic type pressurized cylinder supplements the longitudinal section that is formed on main body outside with safety check.
In figure:
1: main body, 2: action piston, 3: piston, 4: charged piston, 5: non-return projection, 6: guiding valve, 7: hydraulic back-pressure valve, 8,9: pneumatics safety check, 10,20,30,40,50,60,70: pneumatics passage, 11,22,22a, 33: spring, 12: boring, 15: retreat pneumatics operating chamber, 25: the pneumatics operating chamber of advancing, 35: hydraulic booster operating chamber, 45: hydraulic operation chamber, 55,65,75: pneumatics operating chamber
Embodiment
Fig. 1 to Fig. 8 is the schematic diagram of hydraulic type pressurized cylinder according to an embodiment of the invention, with reference to described accompanying drawing explanation according to the hydraulic type pressurized cylinder of the present embodiment.
According to hydraulic type pressurized cylinder of the present invention, in body interior, towards the place ahead, be provided with action piston 2, by pneumatics operating chamber 15 supplies that retreat forwards of pneumatics path 10, retreat with pneumatics, by rearward pneumatics operating chamber 25 supplies of advancing of pneumatics passage 20, advance with pneumatics, rear at action piston 2 arranges separately oil pressure supercharging operating chamber 35 with the pneumatics operating chamber 25 of advancing of action piston 2, the charged piston 4 being supported by spring 11 acts on hydraulic operation chamber 45, described hydraulic operation chamber is communicated in hydraulic booster operating chamber 35 by the little boring 12 of bore, described hydraulic type pressurized cylinder comprises the piston 3 being supported by spring 11, the boring 12 that bore is little, the charged piston 4 of the inside of penetrating action piston 2, control the guiding valve 6 of charged piston 4, the non-return projection 5 that is supported and optionally contact with charged piston 4 by spring 33, pneumatics safety check 8, 9 and pneumatics loop (following, be called main valve).The hydraulic back-pressure valve 7 being supported by spring 22 is formed between hydraulic booster operating chamber 35 and hydraulic operation chamber 45, and when charged piston 4 retreats, described hydraulic back-pressure valve supplements hydraulic oil from hydraulic operation chamber 45 to hydraulic booster operating chamber 35.
Fig. 1 is the longitudinal section schematic diagram of hydraulic type pressurized cylinder inside while retreating, retreat pneumatics and act on action piston 2 and make to move piston 2 and retreat retreating pneumatics operating chamber 15 by pneumatics path 10, and by pneumatics passage 50 and pneumatics passage 40, in pneumatics operating chamber 75, act on guiding valve 6 by safety check 9.Now, by pneumatics passage 20, discharge the pneumatics of the pneumatics operating chamber 25 of advancing.
The longitudinal section schematic diagram that when Fig. 2 is low-load, hydraulic type pressurized cylinder advances at utmost speed, the pneumatics that advances acts on action piston 2 by pneumatics passage 20 in the pneumatics operating chamber 25 of advancing to be made to move piston 2 and advances, and then by pneumatics passage 60, in pneumatics operating chamber 65, acts on guiding valve 6.Now, by non-return projection 5, slowly discharge the pneumatics and the pneumatics that retreats pneumatics operating chamber 15 of pneumatics operating chamber 75.
As shown in Figure 3, under the state that pneumatics at action piston 2 by the pneumatics operating chamber 25 of advancing advances, by non-return projection 5, gently discharge the pneumatics of pneumatics operating chamber 75, when the pressure (pneumatics * kick sectional area) of pneumatics operating chamber 65 is greater than the pressure (pneumatics * large projection sectional area) of pneumatics operating chamber 75, guiding valve 6 moves, now, pneumatics flow into pneumatics operating chamber 55 by pneumatics passage 60, by the effect of pneumatics operating chamber 55, charged piston 4 12 acts on hydraulic booster operating chamber 35 by holing, now the pressure rise of the hydraulic oil of hydraulic booster operating chamber 35 and act on action piston 2.Now, non-return projection 5 is by spring 33 blocking-up pneumatics passages 40.
As shown in Figure 4, under the state that pneumatics at action piston 2 by the pneumatics operating chamber 25 of advancing advances, charged piston 4 moves on and gets through pneumatics operating chamber 55 and pneumatics passage 30, and now, pneumatics flow into pneumatics operating chamber 75 by pneumatics passage 30, pneumatics safety check 8 and pneumatics passage 50.
As shown in Figure 5, under the state that pneumatics at action piston 2 by the pneumatics operating chamber 25 of advancing advances, by pneumatics safety check 8 and pneumatics passage 50, to pneumatics operating chamber 75, flow into pneumatics, when the pressure (pneumatics * large projection sectional area) of pneumatics operating chamber 75 is greater than the pressure (pneumatics * kick sectional area) of pneumatics operating chamber 65, guiding valve 6 moves and discharges the pneumatics of pneumatics operating chamber 55 by pneumatics passage 70, thereby charged piston 4 is retreated by the tension force of spring 11, now, if the pressure of hydraulic booster operating chamber 35 is lower than the pressure of hydraulic operation chamber 45, the hydraulic oil supplementing in hydraulic operation chamber 45 to hydraulic booster operating chamber 35 by safety check 7.
As shown in Figure 6, under the state that the pneumatics at action piston 2 by the pneumatics operating chamber 25 of advancing advances, charged piston 4 retreats and touches non-return projection 5, now, pneumatics passage 40 and pneumatics operating chamber 75 are connected, thereby, by the pneumatics of pneumatics passage 40 discharge pneumatics operating chamber 75.
As shown in Figure 7, under the state that pneumatics at action piston 2 by the pneumatics operating chamber 25 of advancing advances, while discharging the pneumatics of pneumatics operating chamber 75 by pneumatics passage 40, pressure by pneumatics operating chamber 65, guiding valve 6 moves and gets through pneumatics passage 60 and pneumatics operating chamber 65, flow into the Pneumatic action of pneumatics passage 60 in pneumatics operating chamber 55, thereby charged piston 4 advances.As mentioned above, charged piston 4 continues to move back and forth (taking out pump) until action piston 2 advances to finally, form pneumatics safety check 9 so that charged piston 4 is blocked pneumatics passage 40 and pneumatics operating chamber while advancing, thereby, when emergency, to pneumatics operating chamber 75, flow into and retreat pneumatics.
As shown in Figure 8, the hydraulic back-pressure valve 7a being supported by spring 22a is formed at the outside of main body 1 and gets through hydraulic booster operating chamber 35 and hydraulic operation chamber 45, wherein, when charged piston 4 retreats, described hydraulic back-pressure valve supplements hydraulic oil from hydraulic operation chamber 45 to hydraulic booster operating chamber 35.

Claims (6)

1. a hydraulic type pressurized cylinder, it is characterized in that, in body interior, towards the place ahead, be provided with action piston (2), by pneumatics passage (10) pneumatics operating chamber (15) supply that retreats forwards, retreat with pneumatics, by rearward pneumatics operating chamber (25) supply of advancing of pneumatics passage (20), advance with pneumatics, rear at action piston (2) arranges separately oil pressure supercharging operating chamber (35) with the pneumatics operating chamber (25) of advancing of action piston (2), the charged piston (4) being supported by spring (11) acts on hydraulic operation chamber (45), described hydraulic operation chamber is communicated in hydraulic booster operating chamber (35) by the little boring of bore (12), described hydraulic type pressurized cylinder comprises the piston (3) being supported by spring (11), the boring that bore is little (12), the charged piston (4) of the inside of penetrating action piston (2), control the guiding valve (6) of charged piston (4), the non-return projection (5) that is supported and optionally contact with charged piston (4) by spring (33), pneumatics safety check (8, 9) and pneumatics loop, the hydraulic back-pressure valve (7) being supported by spring (22) is formed between hydraulic booster operating chamber (35) and hydraulic operation chamber (45), when charged piston (4) retreats, described hydraulic back-pressure valve supplements hydraulic oil from hydraulic operation chamber (45) to hydraulic booster operating chamber (35).
2. hydraulic type pressurized cylinder according to claim 1, is characterized in that, in order to control charged piston (4), at the rear of main body (1), comprising: pneumatics operating chamber (65), is communicated in pneumatics passage (60), non-return projection (5), by spring (33), supported, and between pneumatics passage (40) and pneumatics operating chamber (75), be optionally contacted with charged piston (4) and control pneumatics passage, pneumatics charged piston (4) by pneumatics operating chamber (55) moves, thereby optionally open and close pneumatics passage (30), described pneumatics passage (30) is communicated in pneumatics operating chamber (75) by pneumatics safety check (8) and pneumatics passage (50), the volume of pneumatics operating chamber (65) is less, the volume of pneumatics operating chamber (75) is relatively large, and comprise and pneumatics operating chamber (65, 75) the pneumatics passage (70) being optionally communicated with.
3. hydraulic type pressurized cylinder according to claim 2, it is characterized in that, the pneumatics passage (30) of optionally opening and closing according to the position of charged piston (4) in pneumatics operating chamber (55) is communicated in the pneumatics operating chamber (75) of guiding valve (6) by pneumatics safety check (8) and pneumatics passage (50).
4. hydraulic type pressurized cylinder according to claim 1, it is characterized in that, the hydraulic back-pressure valve (7) being supported by spring (22) is formed between hydraulic booster operating chamber (35) and hydraulic operation chamber (45), when charged piston (4) retreats, described hydraulic back-pressure valve supplements hydraulic oil from hydraulic operation chamber (45) to hydraulic booster operating chamber (35).
5. hydraulic type pressurized cylinder according to claim 1, it is characterized in that, the hydraulic back-pressure valve (7a) being supported by spring (22a) is formed at the outside of main body (1) and is communicated with hydraulic booster operating chamber (35) and hydraulic operation chamber (45), when charged piston (4) retreats, described hydraulic back-pressure valve supplements hydraulic oil from hydraulic operation chamber (45) to hydraulic booster operating chamber (35).
6. hydraulic type pressurized cylinder according to claim 1, it is characterized in that, at the pneumatics passage (50) that retreats pneumatics operating chamber (15) and be communicated with pneumatics operating chamber (75), be formed with pneumatics safety check (9), thereby, during emergent stopping, retreat pneumatics and flow into pneumatics operating chamber (75).
CN201280051849.0A 2011-10-21 2012-10-19 Hydraulic pressure booster cylinder Pending CN103958947A (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
KR1020110107762A KR101331764B1 (en) 2011-10-21 2011-10-21 Hydraulic Booster Cylinder
KR10-2011-0107762 2011-10-21
PCT/KR2012/008609 WO2013058602A2 (en) 2011-10-21 2012-10-19 Hydraulic pressure booster cylinder

Publications (1)

Publication Number Publication Date
CN103958947A true CN103958947A (en) 2014-07-30

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Application Number Title Priority Date Filing Date
CN201280051849.0A Pending CN103958947A (en) 2011-10-21 2012-10-19 Hydraulic pressure booster cylinder

Country Status (4)

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JP (1) JP2014532843A (en)
KR (1) KR101331764B1 (en)
CN (1) CN103958947A (en)
WO (1) WO2013058602A2 (en)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105003472A (en) * 2015-06-05 2015-10-28 武汉工程大学 Novel gas-liquid pressure cylinder
CN105033720A (en) * 2015-06-29 2015-11-11 沈阳海克机床有限公司 Automatic knife unloading device of rocker arm drill press spindle
CN105570207A (en) * 2016-03-14 2016-05-11 匡信机械(昆山)有限公司 Continuous multi-stage pressurizing method and continuous multi-stage pressurizing cylinder structure

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103982474B (en) * 2014-05-28 2016-05-11 苏州艾酷玛赫设备制造有限公司 Novel gas-liquid power cylinder
KR20160079217A (en) 2014-12-26 2016-07-06 주재석 Hydraulic Pressure Boosting Clinder
CN108757598B (en) * 2018-07-02 2024-08-09 山东大未来机械装备有限公司 Pressurizing cylinder

Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4288987A (en) * 1978-11-11 1981-09-15 Eugen Rapp Pneumo-hydraulic booster with rapid-traverse feature
US5381661A (en) * 1992-07-02 1995-01-17 Tox-Pressotechnik Gmbh Hydraulic pressure transformer
WO1995013478A1 (en) * 1993-11-09 1995-05-18 Valavaara Viljo K Two-stage pressure cylinder
KR19990030918A (en) * 1997-10-02 1999-05-06 주재석 Co-operated reciprocating piston unit
KR20000031529A (en) * 1998-11-04 2000-06-05 주재석 Hydraulic cylinder
CN1418291A (en) * 2000-03-15 2003-05-14 朱宰硕 Hydraulic pressure booster cylinder
CN2743588Y (en) * 2004-10-25 2005-11-30 蔡英泳 Gas liquid force increasing cylinder
CN101421522A (en) * 2006-04-12 2009-04-29 朱瑛暾 Hydraulic pressure transformers
KR20110070951A (en) * 2009-12-19 2011-06-27 주재석 Fluid pressure cylinder with booster pump
KR20110074815A (en) * 2009-12-26 2011-07-04 주재석 Oil pressure generating apparatus

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Publication number Priority date Publication date Assignee Title
JPS53102474A (en) * 1977-02-21 1978-09-06 Onodani Kikou Kk Booster
JPS56147901A (en) * 1980-04-14 1981-11-17 Oigen Ratsupu Pressure conversion hydraulic-pneumatic driver
JPS6123922Y2 (en) * 1981-05-18 1986-07-18
JPS5977109A (en) * 1983-09-21 1984-05-02 Takahata Kenichi Air driving device

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4288987A (en) * 1978-11-11 1981-09-15 Eugen Rapp Pneumo-hydraulic booster with rapid-traverse feature
US5381661A (en) * 1992-07-02 1995-01-17 Tox-Pressotechnik Gmbh Hydraulic pressure transformer
WO1995013478A1 (en) * 1993-11-09 1995-05-18 Valavaara Viljo K Two-stage pressure cylinder
KR19990030918A (en) * 1997-10-02 1999-05-06 주재석 Co-operated reciprocating piston unit
KR20000031529A (en) * 1998-11-04 2000-06-05 주재석 Hydraulic cylinder
CN1418291A (en) * 2000-03-15 2003-05-14 朱宰硕 Hydraulic pressure booster cylinder
CN2743588Y (en) * 2004-10-25 2005-11-30 蔡英泳 Gas liquid force increasing cylinder
CN101421522A (en) * 2006-04-12 2009-04-29 朱瑛暾 Hydraulic pressure transformers
KR20110070951A (en) * 2009-12-19 2011-06-27 주재석 Fluid pressure cylinder with booster pump
KR20110074815A (en) * 2009-12-26 2011-07-04 주재석 Oil pressure generating apparatus

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105003472A (en) * 2015-06-05 2015-10-28 武汉工程大学 Novel gas-liquid pressure cylinder
CN105033720A (en) * 2015-06-29 2015-11-11 沈阳海克机床有限公司 Automatic knife unloading device of rocker arm drill press spindle
CN105570207A (en) * 2016-03-14 2016-05-11 匡信机械(昆山)有限公司 Continuous multi-stage pressurizing method and continuous multi-stage pressurizing cylinder structure
CN105570207B (en) * 2016-03-14 2017-06-06 匡信机械(昆山)有限公司 A kind of continous way multi-stage booster method and its supercharging cylinder structure

Also Published As

Publication number Publication date
KR20130043712A (en) 2013-05-02
KR101331764B1 (en) 2013-11-20
JP2014532843A (en) 2014-12-08
WO2013058602A2 (en) 2013-04-25
WO2013058602A3 (en) 2013-07-04

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