CN101421522A - Hydraulic pressure transformers - Google Patents
Hydraulic pressure transformers Download PDFInfo
- Publication number
- CN101421522A CN101421522A CNA2007800133872A CN200780013387A CN101421522A CN 101421522 A CN101421522 A CN 101421522A CN A2007800133872 A CNA2007800133872 A CN A2007800133872A CN 200780013387 A CN200780013387 A CN 200780013387A CN 101421522 A CN101421522 A CN 101421522A
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- China
- Prior art keywords
- air pressure
- operating cavity
- backward
- path
- travels forward
- 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
- F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
- F15B11/06—Servomotor systems without provision for follow-up action; Circuits therefor involving features specific to the use of a compressible medium, e.g. air, steam
- F15B11/072—Combined pneumatic-hydraulic systems
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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
- F15B3/00—Intensifiers or fluid-pressure converters, e.g. pressure exchangers; Conveying pressure from one fluid system to another, without contact between the fluids
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
- F15B2211/214—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being hydrotransformers
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
- F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
- F15B2211/216—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being pneumatic-to-hydraulic converters
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/32—Directional control characterised by the type of actuation
- F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/30—Directional control
- F15B2211/35—Directional control combined with flow control
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/605—Load sensing circuits
- F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/60—Circuit components or control therefor
- F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
- F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
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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
- F15B2211/00—Circuits for servomotor systems
- F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
- F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
- F15B2211/7051—Linear output members
- F15B2211/7055—Linear output members having more than two chambers
Abstract
The present invention relates to a hydraulic pressure intensifier that has all of the advantages of the pneumatic cylinder and the hydraulic cylinder and includes first operating chambers, a hydraulic operating chamber, front and back operating chambers, and second operating chambers formed sequentially from the front side thereof. The front and back operating chambers and the hydraulic operating chambers are connected through an excess flow bore, and an operating rod is moved forwardly by the supply of the air pressure to the first operating chambers and the front and back operating chambers. Then, only upon the application of a high load the air pressure is selectively supplied to the second forwardly moving operating chamber through a pilot valve and a master valve, thereby generating a high pressure in the hydraulic operating chamber.
Description
Technical field
The present invention relates to a kind of hydraulic intensifier, relate more specifically to a kind of hydraulic intensifier that is widely used in various industrial fields, it can improve the performance and the output of pneumatic cylinder.
Background technique
Pneumatic cylinder and oil hydraulic cylinder are mainly used in and apply pressurized energy, therefore are used to clamp device, compression set, oblique drawing device (cocking device) etc.Clamp device or compression set do not need steering force when beginning to operate, but need relatively large steering force when end operation.Therefore, be used to apply given stressed these cylinders much bigger steering force should be provided in the ending phase of extrusion piston bar.
For this reason, adopt the excessive cylinder of diameter and weight, obtain necessary big steering force with ending phase at the extrusion piston bar.Yet under the situation of using diameter and the very large cylinder of weight, service speed is relatively low, thereby reduces working efficiency, and needs a large amount of air pressure or hydraulic oil, thereby causes that energy loss and cost consumption increase.
In order to address these problems, a kind of conventional cylinder has been proposed, wherein pressurized machine links to each other with pipeline from air pressure to cylinder that supply oil pressure or, thereby applies very high pressure in the ending phase of extrusion piston bar, thereby increases steering force in the ending phase of piston rod.
Yet, because this requires conventional cylinder should have the structure of relative complex, and comprises electronic valve, displacement pump and control unit more than four, so its become costliness and failure rate height.
Summary of the invention
Technical problem
Therefore, the present invention is devoted to solve the problem that occurs in the conventional hydraulic pressure intensifier, and the object of the present invention is to provide a kind of hydraulic intensifier, but has high output although this hydraulic intensifier size is little, have high energy efficiency and have the structure of simplification, and carry out in mode more fast and accurately and to strengthen operation and motor performance backward, thereby strengthen performance accuracy and prevent to produce fault.
Technological scheme
To achieve these goals, according to the present invention, a kind of hydraulic intensifier is provided, this hydraulic intensifier comprises: first operating cavity, this first operating cavity has air pressure path of motion backward that forms in its front side and the air pressure path that travels forward that forms at its rear side, and having layout operated piston within it, this operated piston has from its outwardly directed operating stem; The hydraulic operation chamber is furnished with the guide rod in the rear side formation of described operated piston in this hydraulic operation chamber; A plurality of operating cavity, described operating cavity have the piston that week arranges in it, and the rear side that is connected to described hydraulic operation chamber in described operating cavity front side is formed with the air pressure path that travels forward to form oil pressure at this piston rear side; A plurality of second operating cavity, in described second operating cavity, be furnished with charged piston, this charged piston has be suitable for passing this piston with booster rod that moves forward and backward and the spring of arranging around the periphery of this booster rod, the air pressure path that travels forward that described second operating cavity has the air pressure path that is formed on its front side and is formed on its rear side in described hydraulic operation chamber; And main valve, this main valve is connected to the air pressure path that travels forward of described second operating cavity, and spool pin (spool pin) order that is arranged within it is separated into: the operating cavity that travels forward is formed with the air pressure inlet that travels forward on it; Motion discharge chamber backward is formed with motion air pressure outlet backward on it; Motor performance chamber backward, its front side is formed with the air pressure inside path; And enhancing operating cavity, this enhancing operating cavity is connected to control valve or the safety check that is arranged in the described air pressure of motion backward path place, make that described spool pin is moved backward to block the described air pressure path that travels forward during initially the travelling forward of described operating stem, the oil pressure of the described operating cavity that travels forward is higher than described enhancing operating cavity so that described spool pin travels forward when applying high loading, thereby oil pressure is delivered to the described air pressure path that travels forward, and described spool pin is returned its initial position when described operating stem moves backward.
On the other hand, described main valve and described control valve or safety check and hydraulic intensifier body are integrally formed or separate formation with the hydraulic intensifier body.
In addition, described piston has safety check and seal ring, and this safety check is suitable for preventing that the air pressure of its rear side is supplied to its front side, and the sealing ring is suitable for sealing the oil that is supplied to this piston.
Beneficial effect
According to the present invention, a kind of hydraulic intensifier is provided, this hydraulic intensifier does not strengthen operation when applying low load, but strengthens operation when applying high loading, thereby reduces air consumption and make the operating time minimum.
Description of drawings
Fig. 1 is the longitudinal section of expression according to the structure of the hydraulic intensifier that is built-in with main valve of first embodiment of the invention;
Fig. 2 is the longitudinal section of expression according to the motion state backward of the hydraulic intensifier of first embodiment of the invention;
Fig. 3 is expression according to the longitudinal section of the low loaded-up condition during operation that travels forward of the hydraulic intensifier of first embodiment of the invention;
Fig. 4 is the longitudinal section according to the high loading state of the hydraulic intensifier of first embodiment of the invention;
Fig. 5 is the longitudinal section of formation according to the motion state backward of the control valve of the hydraulic intensifier of first embodiment of the invention;
Fig. 6 is expression according to the longitudinal section of the low loaded-up condition during operation that travels forward of the control valve of the hydraulic intensifier of first embodiment of the invention;
Fig. 7 is expression according to the longitudinal section of the high loading state during operation that travels forward of the control valve of the hydraulic intensifier of first embodiment of the invention;
Fig. 8 is the longitudinal section of expression according to the structure of the hydraulic intensifier of second embodiment of the invention, wherein is connected with safety check and replaces control valve;
Fig. 9 is the longitudinal section of expression according to the structure of the hydraulic intensifier of third embodiment of the invention, under its China and foreign countries' state that main valve is arranged on control valve connects; And
Figure 10 is the longitudinal section of expression according to the structure of the hydraulic intensifier of four embodiment of the invention, under its China and foreign countries' state that main valve is arranged on safety check connects.
The explanation of the reference character of critical piece among the figure
1: body 10a, 10b: first operating cavity
11: operating stem 13: operated piston
20: hydraulic operation chamber 21: guide rod
23: overflow hole 30a, 30b: operating cavity
33: piston 40a, 40b: second operating cavity
41: booster rod 42: spring
43: charged piston 46: the air pressure path travels forward
60: main valve 62: spool pin
70: control valve 71: operative pin
Embodiment
Below, the preferred implementation that present invention will be described in detail with reference to the accompanying.
Fig. 1 to Fig. 7 shows the hydraulic intensifier that is built-in with main valve according to first embodiment of the invention.
First embodiment of the invention, as shown in Figures 1 to 4, this hydraulic intensifier comprises: first operating cavity 10a and the 10b that is provided with operated piston 13 in it; Be provided with the hydraulic operation chamber 20 of guide rod 21 in it; Operating cavity 30a and 30b, they are connected to the rear side in hydraulic operation chamber 20, and are provided with piston 33 week in it; Be provided with second operating cavity 40a and the 40b of charged piston 43 in it, charged piston 43 has booster rod 41, and booster rod 41 is suitable for passing piston 33, is used for seesawing in hydraulic operation chamber 20, and is provided with spring 42 around its periphery; Be arranged in the main valve 60 of the second operating cavity 40a (hereinafter referred to as second operating cavity that travels forward) rear side, main valve 60 is formed on the rear portion of charged piston 43, is used to control be supplied to second the travel forward air pressure of operating cavity 40a and from second the flowing of air pressure that travels forward operating cavity 40a discharging; And be installed in main valve 60 sentence control main valve 60 control valve 70.
At first, the first operating cavity 10a and 10b are formed on the front side of body 1, and have the operated piston 13 that sets within it, the guide rod 21 that operated piston 13 has towards its front side outwardly directed operating stem 11 and stretches out backward towards the inboard in hydraulic operation chamber 20.The formation of operated piston 13 makes the operating cavity 10b that wins be restricted to the first motor performance chamber 10b and make the first operating cavity 10a be restricted to the first operating cavity 10a that travels forward backward.Therefore, first backward the front side of motor performance chamber 10b be provided with motion air pressure path 15 backward, be provided with the air pressure path 17 that travels forward at first rear side that travels forward operating cavity 10a.
Moreover hydraulic operation chamber 20 has the guide rod 21 that sets within it, and is connected to preceding operating cavity 30a by the overflow hole 23 that is arranged on its rear side, the hydraulic oil deficiency of operating cavity 30a before being used for preventing when producing enhancing pressure.
On the other hand, piston 33 has grease proofing intrusion chamber 38, thereby prevent that the air pressure among the operating cavity 30b of back from flowing into preceding operating cavity 30a, grease proofing intrusion chamber 38 is provided with safety check 36 in the part that links to each other with preceding operating cavity 30b, and bubble-tight mode is provided with seal ring 37 in it in both sides to keep.
And the second operating cavity 40a that travels forward is connected to the main valve 60 that is suitable for by control valve 70 control at its rear side.The air pressure that will travel forward when main valve 60 applies high loading during travelling forward inlet 61a is connected with the air pressure path 46 that travels forward, and discharges and is applied to second air pressure that travels forward operating cavity 40a exporting 61b by motion air pressure backward between moving period backward.
To shown in Figure 7, main valve 60 is separated into successively by the spool pin 62 that sets within it as Fig. 5: the operating cavity 63 that travels forward, supply the air pressure that travels forward separately to it; Motion discharge chamber backward 64 is being passed from motion discharge chamber backward 64 from second air pressure that travels forward operating cavity 40a discharging between moving period backward; The motor performance chamber 65 backward, and it has the air pressure inside path 65a that is formed on its front side, are used to make the air pressure of motion backward to flow to it; And strengthening operating cavity 68, it is connected to and is arranged in the control valve 70 at motion air pressure path 66 places backward.Spool pin 62 has a plurality of stuffer 62a, and these stuffers are arranged to closely contact with the inwall of main valve 60 along its periphery, are used to seal each operating cavity.
For the operation of above-mentioned main valve 60, backward between moving period, crossing air pressure inside path 65a and 69 by the Pneumatic pipe cleaner of control valve 70 supply is sent to and strengthens operating cavity 68 and motor performance chamber 65 backward, thereby Move Volumes pivot pin 62, make travel forward air pressure path 46 and backward motion air pressure export 61b and be connected with each other.
So, during travelling forward, apply when hanging down load, staying Pneumatic pipe cleaner in the motor performance chamber 65 backward crosses air pressure inside path 65a and slowly is disposed to motion air pressure path 66 backward, if and the air pressure that is supplied to the air pressure inlet 61a that travels forward increases, make sectional area less than the approaching air pressure that strengthens in the operating cavity 68 of the air pressure in the operating cavity 63 that travels forward that strengthens operating cavity 68, then spool pin 62 is moved along the direction opposite with it, and the feasible air pressure inlet 61a that travels forward is communicated with the air pressure path 46 that travels forward.Therefore, the air pressure that travels forward flow into second travel forward operating cavity 40a so that charged piston 43 travel forward, thereby allow overflow hole 23 to get clogged in hydraulic operation chamber 20, to strengthen operation.
And the air pressure path 35 that travels forward is connected to the pressure generator that travels forward, and motion air pressure path 15 is connected to motion pressure generator backward backward.
Under the situation of above-mentioned structure, below the operation according to hydraulic intensifier of the present invention is described.
At first at motion backward, by motion air pressure path 15 backward to the first motor performance chamber 10b supply air pressure backward, thereby operated piston 13 is moved backward, supply air pressure to the air pressure of the motion backward path 66 of control valve 70 simultaneously, thereby promote the valve piston 73 and the operative pin 71 of valve operating cavity 74.The result, Pneumatic pipe cleaner is crossed backward motion air pressure path 66 and air pressure inside path 69 and 65a and is sent to and strengthens operating cavity 68 and motor performance chamber 65 backward, thereby promote spool pin 62 downwards, make travel forward air pressure path 46 and backward motion air pressure outlet 61b communicate with each other, thereby from second backward motor performance chamber 40a discharge air pressure.At this moment, charged piston 43 moves backward by spring 42 and is in Fig. 2 and state shown in Figure 5.
Next, travelling forward according to hydraulic intensifier of the present invention is described.
If under state shown in Figure 2, supply the air pressure that travels forward by the air pressure path 35 that travels forward that is formed on body 1 middle part, then air pressure at first is sent to the operating cavity 30b that travels forward, thereby move forward piston 33, then Pneumatic pipe cleaner is crossed the air pressure path 17 that travels forward and is sent to the first operating cavity 10a that travels forward, thereby moves forward operated piston 13.
At this moment, owing to no longer supply motion air pressure backward, Pneumatic pipe cleaner in the chamber of motor performance backward 65 of air pressure in the valve operating cavity 74 of control valve 70 and main valve 60 is crossed backward, and motion air pressure path 66 is discharged, make operative pin 71 by spring 75 motions, closely contact with the body of control valve 70 with permission stuffer 72, thereby block motion air pressure path 66 and air pressure inside path 69 backward.
As a result, the air pressure that enhancing operating cavity 68 is held back is sent to the front side of spool pin 62, thereby is sent to the operating cavity 63 that travels forward although the Pneumatic pipe cleaner that travels forward is crossed the air pressure inlet 61a that travels forward, and spool pin 62 is also motionless at all, as shown in Figure 6.
Therefore, the air pressure that the travels forward inlet 61a and the air pressure path 46 that travels forward get clogged, and make air pressure can not be sent to the second operating cavity 40a that travels forward, and this makes charged piston 43 remain on halted state, as shown in Figure 3.
Afterwards, operated piston 13 travels forward, and if operating stem 11 at its front end against manipulating object but without undergoing load, then operated piston 13 time-outs and piston 33 also suspend, the air pressure that making wins travels forward among operating cavity 10a and the back operating cavity 30b continues to raise, and the air pressure in the operating cavity 63 that travels forward of main valve 60 also raises simultaneously.
Air pressure if travel forward in the operating cavity 63 is increased near the air pressure that strengthens in the operating cavity 68, and then because the sectional area of the operating cavity 63 that travels forward is slightly larger than the sectional area that strengthens operating cavity 68, thereby spool pin 62 moves.Therefore, strengthen Pneumatic pipe cleaner in the operating cavity 68 and cross backward that motor performance chamber 65 is disposed to motion air pressure path 66 backward, and spool pin 62 is raised up to its end that rises.
Therefore, as shown in Figure 7, the air pressure that the travels forward inlet 61a and the air pressure path 46 that travels forward communicate with each other, and the air pressure that travels forward is sent to the second operating cavity 40a that travels forward, make booster rod 41 pass overflow hole 23, simultaneously the oil pressure in hydraulic operation chamber 20 raises and applies very big power to the front end of operating stem 11.
On the other hand, Fig. 8 shows the hydraulic intensifier according to second embodiment of the invention, and wherein main valve 60 is integrally formed with body 1, and safety check 76 replaces described control valve is connected to main valve 60 as the parts that separate with body 1 enhancing operating cavity 68.In addition, the air pressure inside path 65a that links to each other with motor performance chamber 65 backward is connected to the rear end of safety check 76.In this case, the operation of second embodiment of the invention is identical with the operation of first embodiment of the invention, for of the present invention the omission for purpose of brevity is described.
Fig. 9 shows the hydraulic intensifier according to third embodiment of the invention, wherein main valve 60 and control valve 70 separate formation with body 1, and reference character 45 is represented and is connected to the air pressure path that travels forward that the second air pressure path 46 that travels forward that travels forward operating cavity 40a links to each other.
Figure 10 shows the hydraulic intensifier according to four embodiment of the invention, and wherein main valve 60 and safety check 76 separate formation with body 1.
Claims (7)
1, a kind of hydraulic intensifier, this hydraulic intensifier comprises:
First operating cavity, this first operating cavity have air pressure path of motion backward that forms in its front side and the air pressure path that travels forward that forms at its rear side, and have layout operated piston within it, and this operated piston has from its outwardly directed operating stem;
The hydraulic operation chamber is furnished with the guide rod in the rear side formation of described operated piston in this hydraulic operation chamber;
A plurality of operating cavity, described operating cavity have the piston that week arranges in it, and the rear side that is connected to described hydraulic operation chamber in described operating cavity front side is formed with the air pressure path that travels forward to form oil pressure at this piston rear side;
A plurality of second operating cavity, in described second operating cavity, be furnished with charged piston, this charged piston has be suitable for passing this piston with booster rod that moves forward and backward and the spring of arranging around the periphery of this booster rod, the air pressure path that travels forward that described second operating cavity has the air pressure path that is formed on its front side and is formed on its rear side in described hydraulic operation chamber; And
Main valve, this main valve is connected to the air pressure path that travels forward of described second operating cavity, and be furnished with spool pin in it, this spool pin is suitable for controlling by control valve or safety check, thereby when initially the travelling forward of described operating stem, under the effect of air pressure inside, described control valve or closure of check ring and described spool pin are blocked the described air pressure path that travels forward, when during travelling forward, applying high loading, described air pressure inside is discharged so that described spool pin is opened the described air pressure path that travels forward, thereby the air pressure that will travel forward is delivered to described second operating cavity, produces the pressure that strengthens whereby.
2, hydraulic intensifier according to claim 1, wherein said main valve are arranged spool pin within it and a plurality of stuffers of forming along the periphery of this spool pin are separated in proper order: the operating cavity that travels forward is formed with the air pressure inlet that travels forward on it; Motion discharge chamber backward is formed with motion air pressure outlet backward on it; Motor performance chamber backward, its front side is formed with the first air pressure inside path, and this first air pressure inside path links to each other with motion air pressure path backward; And enhancing operating cavity, this enhancing operating cavity is connected to described control valve or the safety check that is arranged in the described air pressure of motion backward path place, and size is less than the described operating cavity that travels forward, make that described spool pin is moved backward to block the described air pressure path that travels forward during initially the travelling forward of described operating stem, the oil pressure of the described operating cavity that travels forward is higher than described enhancing operating cavity so that described spool pin travels forward when applying high loading, thereby oil pressure is disposed to the described first air pressure inside path from described enhancing operating cavity by described motor performance backward chamber, and the described air pressure path that travels forward is connected with the described air pressure inlet of travelling forward, and the motion oil pressure is sent to described motor performance backward chamber backward when described operating stem moves backward, thereby makes described spool pin return its initial position.
3, hydraulic intensifier according to claim 2, the described control valve that wherein is connected to described main valve has: the valve piston that is arranged in the side in its valve operating cavity; Stuffer, this stuffer are arranged in the opposite side in the described valve operating cavity, thereby closely contact with the interior plane of inclination of described valve operating cavity or separate, and are used for connecting or blocking described air pressure path of motion backward and described enhancing operating cavity; And operative pin, this operative pin has the spring of arranging along the periphery at the rear portion of described stuffer; This control valve is connected to the second air pressure inside path that is communicated with the enhancing operating cavity of described main valve and the described first air pressure inside path in described motor performance backward chamber in both sides.
4, hydraulic intensifier according to claim 1 and 2, the described enhancing operating cavity of wherein said main valve is connected to a safety check, and the described first air pressure inside path that links to each other with described motor performance backward chamber is connected to the rear end of described safety check.
5, hydraulic intensifier according to claim 1 and 2, wherein said main valve and described control valve or safety check and hydraulic intensifier body are integrally formed or separate formation with the hydraulic intensifier body.
6, hydraulic intensifier according to claim 1, wherein said hydraulic operation chamber has the overflow hole that is arranged in its rear side, is used for preventing the hydraulic oil deficiency of described preceding operating cavity when producing high loading.
7, hydraulic intensifier according to claim 1, wherein said piston comprise the grease proofing intrusion chamber that is formed by safety check and seal ring.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| KR1020060033350A KR100704958B1 (en) | 2006-04-12 | 2006-04-12 | Hydraulic pressure transformers |
| KR1020060033350 | 2006-04-12 |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101421522A true CN101421522A (en) | 2009-04-29 |
Family
ID=38161191
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNA2007800133872A Pending CN101421522A (en) | 2006-04-12 | 2007-04-06 | Hydraulic pressure transformers |
Country Status (3)
| Country | Link |
|---|---|
| KR (1) | KR100704958B1 (en) |
| CN (1) | CN101421522A (en) |
| WO (1) | WO2007117099A1 (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102597535A (en) * | 2009-10-13 | 2012-07-18 | 金基赞 | Actuator using pneumatic pressure and hydraulic pressure |
| CN103958947A (en) * | 2011-10-21 | 2014-07-30 | 朱多暎 | Hydraulic pressure booster cylinder |
| CN105952698A (en) * | 2016-06-17 | 2016-09-21 | 武汉软件工程职业学院 | Gas-liquid pressurized cylinder |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR101092185B1 (en) | 2011-06-01 | 2011-12-26 | 김형동 | Booster apparatus using two pressure air booster |
| KR101339921B1 (en) | 2011-09-28 | 2013-12-10 | 주재석 | Hydraulic device for hydraulic cylinders |
| KR101655420B1 (en) * | 2013-03-04 | 2016-09-22 | 주식회사 하이시스 | Hydraulic Power Cylinder with Booser Pump Equipment |
| KR101712262B1 (en) | 2015-03-27 | 2017-03-03 | 곽창순 | Hydraulic cylinder integrally incoporating buster pump |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US4361000A (en) * | 1981-06-01 | 1982-11-30 | The Toro Company | Bagging filament mower |
| DE3733863C2 (en) * | 1987-10-07 | 1997-09-11 | Teves Gmbh Alfred | Hydraulic booster, in particular for actuating a master brake cylinder of a vehicle brake system |
| KR950007623B1 (en) * | 1987-10-21 | 1995-07-13 | 씨. 소오웨인 알버트 | Fluid pressure intensifier |
| JPH04201616A (en) * | 1990-11-30 | 1992-07-22 | Nissan Motor Co Ltd | Pressure control valve for active suspension |
| WO1992011993A1 (en) * | 1991-01-14 | 1992-07-23 | Engel Maschinenbau Gesellschaft Mbh | Device for performing a two-stage linear movement |
| KR100338496B1 (en) * | 1999-10-01 | 2002-05-30 | 주재석 | Hydraulic Pressure Intensifier |
| KR200243058Y1 (en) * | 2001-05-26 | 2001-10-15 | (주)후스 | external transfer valve type intensifier for hydraulic system |
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2006
- 2006-04-12 KR KR1020060033350A patent/KR100704958B1/en not_active IP Right Cessation
-
2007
- 2007-04-06 WO PCT/KR2007/001698 patent/WO2007117099A1/en active Application Filing
- 2007-04-06 CN CNA2007800133872A patent/CN101421522A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102597535A (en) * | 2009-10-13 | 2012-07-18 | 金基赞 | Actuator using pneumatic pressure and hydraulic pressure |
| CN102597535B (en) * | 2009-10-13 | 2016-01-13 | 金基赞 | Utilize the actuator of air pressure and hydraulic pressure |
| CN103958947A (en) * | 2011-10-21 | 2014-07-30 | 朱多暎 | Hydraulic pressure booster cylinder |
| CN105952698A (en) * | 2016-06-17 | 2016-09-21 | 武汉软件工程职业学院 | Gas-liquid pressurized cylinder |
| CN105952698B (en) * | 2016-06-17 | 2019-07-30 | 武汉软件工程职业学院 | A kind of solution-air pressurized cylinder |
Also Published As
| Publication number | Publication date |
|---|---|
| KR100704958B1 (en) | 2007-04-09 |
| WO2007117099A1 (en) | 2007-10-18 |
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Open date: 20090429 |