TWI704292B - Pressure booster - Google Patents
Pressure booster Download PDFInfo
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- TWI704292B TWI704292B TW108129127A TW108129127A TWI704292B TW I704292 B TWI704292 B TW I704292B TW 108129127 A TW108129127 A TW 108129127A TW 108129127 A TW108129127 A TW 108129127A TW I704292 B TWI704292 B TW I704292B
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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
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B7/00—Piston machines or pumps characterised by having positively-driven valving
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/10—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid
- F04B9/109—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers
- F04B9/111—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members
- F04B9/115—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being liquid having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by two single-acting liquid motors, each acting in one direction
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
- F04B9/00—Piston machines or pumps characterised by the driving or driven means to or from their working members
- F04B9/08—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid
- F04B9/12—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air
- F04B9/129—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers
- F04B9/131—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers with two mechanically connected pumping members
- F04B9/135—Piston machines or pumps characterised by the driving or driven means to or from their working members the means being fluid the fluid being elastic, e.g. steam or air having plural pumping chambers with two mechanically connected pumping members reciprocating movement of the pumping members being obtained by two single-acting elastic-fluid motors, each acting in one direction
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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
- F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
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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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
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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
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated 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
- F15B2211/305—Directional control characterised by the type of valves
- F15B2211/30505—Non-return valves, i.e. check valves
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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
- F15B2211/355—Pilot pressure 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
- F15B2211/635—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
- F15B2211/77—Control of direction of movement of the output member
- F15B2211/7725—Control of direction of movement of the output member with automatic reciprocation
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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
- F15B2211/80—Other types of control related to particular problems or conditions
- F15B2211/885—Control specific to the type of fluid, e.g. specific to magnetorheological fluid
- F15B2211/8855—Compressible fluids, e.g. specific to pneumatics
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Pressure Circuits (AREA)
- Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
- Fluid-Driven Valves (AREA)
Abstract
Description
本發明係關於將壓力流體增壓並輸出的增壓裝置。 The present invention relates to a pressurizing device that pressurizes and outputs pressure fluid.
習知技術中,藉由活塞的往復動作連續地將壓力流體增壓並輸出的增壓裝置已為公知。 In the prior art, a pressurizing device that continuously pressurizes and outputs the pressure fluid by the reciprocating action of the piston is known.
例如,日本特開平08-21404號公報記載有一種增壓器,其係將各個活塞直接連結於活塞桿的一對增壓用缸配置成互相面對,且在一對增壓用缸之間設有能量回收用缸。此增壓器係藉由將壓縮空氣注入一方的增壓用缸之壓縮室與動作室以及另一方的增壓用缸之壓縮室,而將已注入一方的增壓用缸之壓縮室的空氣增壓並輸出。對於增壓用缸的給氣切換動作及回對於收用缸的流路切換動作係藉由以簧片開關檢測出增壓用缸的活塞位置且使切換閥的螺線管ON-OFF而進行。 For example, Japanese Patent Application Laid-Open No. 08-21404 describes a supercharger in which a pair of pressure-increasing cylinders in which each piston is directly connected to a piston rod are arranged to face each other, and between the pair of pressure-increasing cylinders Equipped with a cylinder for energy recovery. This supercharger injects compressed air into the compression chamber and action chamber of one supercharging cylinder and the compression chamber of the other supercharging cylinder, and the air that has been injected into the compression chamber of one supercharging cylinder Boost and output. The air supply switching action for the booster cylinder and the flow path switching action for the retracting cylinder are performed by detecting the piston position of the booster cylinder with a reed switch and turning the solenoid of the switching valve ON-OFF. .
日本特開平08-21404號公報的增壓器中,用以驅動活塞的動作室及用以壓縮流體的壓縮室係設於一對增壓用缸,而有限制設計的自由度之疑慮。再者,為了進行切換動作而使用了簧片開關及螺線管,因而必須包含電氣配線的電性手段。 In the supercharger of Japanese Patent Laid-Open No. 08-21404, the action chamber for driving the piston and the compression chamber for compressing the fluid are provided in a pair of pressurizing cylinders, and there is a concern that the degree of freedom of design is limited. Furthermore, reed switches and solenoids are used to perform the switching operation, and therefore, electrical means including electrical wiring must be included.
對此,本案申請人係針對個別設置驅動活塞的缸與壓縮壓力流體的缸並將此等緊密互動性地配置而可不依賴電性手段進行切換動作的增壓裝置之發明,提出了發明專利申請(日本特願2017-164945號)。 In this regard, the applicant in this case filed an invention patent application for the invention of a pressure booster device that separately sets up a cylinder for driving the piston and a cylinder for compressing pressure fluid and arranges these closely interactively without relying on electrical means for switching operations. (Japan Special Application No. 2017-164945).
上述專利申請案的增壓裝置係具備:一對導引閥,係將驅動用缸配設在增壓用缸的兩側,且具備驅動用缸的活塞以其移動端抵接的推桿;及一對動作閥,係切換對於驅動用缸的加壓室之來自壓力流體供給源的壓力流體的供給狀態。 The pressure boosting device of the above patent application is provided with: a pair of pilot valves, the driving cylinder is arranged on both sides of the pressure boosting cylinder, and the piston of the driving cylinder is provided with a push rod abutting with its moving end; And a pair of operating valves switch the supply state of the pressure fluid from the pressure fluid supply source to the pressure chamber of the driving cylinder.
上述專利申請案的增壓裝置中,增壓裝置的輸出接近飽和狀態時,驅動用缸的活塞推壓推桿的力道會變弱,而有在導引閥未充分切換的狀態下,推桿被彈力推回的情形,並非令人滿意。本發明係有鑑於此種情形而研創者,目的在於提供一種增壓裝置,即使在驅動用缸的活塞推壓導引閥的力道較弱時,也可確實地切換導引閥。 In the supercharging device of the aforementioned patent application, when the output of the supercharging device is close to the saturated state, the force of the piston of the driving cylinder to push the push rod will be weakened, and in the state where the pilot valve is not fully switched, the push rod The situation being pushed back by elastic force is not satisfactory. The present invention was developed in view of this situation, and aims to provide a pressure boosting device that can reliably switch the pilot valve even when the force of the piston of the driving cylinder to push the pilot valve is weak.
本發明的增壓裝置係在增壓用缸的兩側配設有驅動用缸,該增壓裝置係具備:一對導引閥,係備有由驅動用缸之活塞以其移動端相抵接的控制銷;及一對動作閥,係切換來自壓力流體供給源的壓力流體對於驅動用缸之加壓室的供給狀態;當活塞推壓控制銷使得一方或另一方的導引閥切換到第一位置時,切換成壓力流體供給到一對動作閥之狀態,且預定的流體壓力係作用於控制銷,使導引閥保持於第一位置。 The pressure boosting device of the present invention is equipped with driving cylinders on both sides of the pressure boosting cylinder. The pressure boosting device is provided with a pair of pilot valves, which are abutted by the piston of the driving cylinder with their moving ends. The control pin; and a pair of action valves, which switch the supply state of the pressure fluid from the pressure fluid supply source to the pressure chamber of the driving cylinder; when the piston pushes the control pin, the pilot valve of one or the other is switched to the first At one position, it is switched to a state where pressure fluid is supplied to a pair of action valves, and a predetermined fluid pressure is applied to the control pin to keep the pilot valve in the first position.
若依據上述增壓裝置,能夠以預定的流體壓力將與驅動用缸之活塞抵接的控制銷推壓到最盡頭,而可將導引閥保持在充分切換的位置。 According to the above-mentioned pressurizing device, the control pin abutting on the piston of the driving cylinder can be pushed to the end with a predetermined fluid pressure, and the pilot valve can be maintained at a fully switching position.
若依據本發明之增壓裝置,因預定的流體壓力作用在控制銷以使導引閥保持在切換後的位置,故即使驅動用缸的活塞推壓控制銷的力道較弱,也可將控制銷推壓到最盡頭,而確實地切換導引閥。 According to the pressurizing device of the present invention, because a predetermined fluid pressure acts on the control pin to keep the pilot valve in the switched position, even if the force of the piston of the driving cylinder to push the control pin is weak, the control can be controlled The pin is pushed to the end, and the pilot valve is surely switched.
由配合附圖進行之以下較佳實施形態例的說明,應可更明瞭上述目的、特徵及優點。 The description of the following preferred embodiments in conjunction with the drawings should clarify the above-mentioned objectives, features and advantages.
10‧‧‧增壓裝置 10‧‧‧Boosting device
12‧‧‧增壓用缸 12‧‧‧Pressurized cylinder
14‧‧‧第一驅動用缸 14‧‧‧The first drive cylinder
16‧‧‧第二驅動用缸 16‧‧‧Second drive cylinder
18‧‧‧第一蓋構件 18‧‧‧First cover member
20‧‧‧第二蓋構件 20‧‧‧Second cover member
22‧‧‧增壓室 22‧‧‧Pressure chamber
22a‧‧‧第一增壓室 22a‧‧‧First pressurization chamber
22b‧‧‧第二增壓室 22b‧‧‧Second plenum
24‧‧‧第一驅動室 24‧‧‧First Drive Room
24a、26a‧‧‧加壓室 24a、26a‧‧‧Pressure chamber
24b、26b‧‧‧背壓室 24b, 26b‧‧‧Back pressure chamber
26‧‧‧第二驅動室 26‧‧‧Second Drive Room
28‧‧‧第三蓋構件 28‧‧‧The third cover member
30‧‧‧壁部 30‧‧‧Wall
32‧‧‧活塞桿 32‧‧‧Piston rod
34‧‧‧增壓用活塞 34‧‧‧Piston for pressurization
36‧‧‧第一驅動用活塞 36‧‧‧Piston for the first drive
38‧‧‧第二驅動用活塞 38‧‧‧Second drive piston
40‧‧‧供給埠 40‧‧‧Supply Port
42a‧‧‧第一供給流路 42a‧‧‧First supply flow path
42b‧‧‧第二供給流路 42b‧‧‧Second supply flow path
42c‧‧‧第一供給逆止閥 42c‧‧‧First supply check valve
42d‧‧‧第二供給逆止閥 42d‧‧‧Second supply check valve
44‧‧‧輸出口 44‧‧‧Output port
46a‧‧‧第一輸出流路 46a‧‧‧First output channel
46b‧‧‧第二輸出流路 46b‧‧‧Second output channel
46c‧‧‧第一輸出逆止閥 46c‧‧‧First output check valve
46d‧‧‧第二輸出逆止閥 46d‧‧‧Second output check valve
48‧‧‧第一動作閥 48‧‧‧First action valve
50‧‧‧第一殼體 50‧‧‧First shell
52‧‧‧第二動作閥 52‧‧‧Second action valve
54‧‧‧第二殼體 54‧‧‧Second shell
56F‧‧‧導引埠 56F‧‧‧ Pilot port
58a至58e‧‧‧流路 58a to 58e‧‧‧Flow path
60‧‧‧第一固定節流閥 60‧‧‧The first fixed throttle
62‧‧‧第一消音器 62‧‧‧First silencer
56A、64A‧‧‧第一埠 56A, 64A‧‧‧First port
56B、64B‧‧‧第二埠 56B, 64B‧‧‧Second port
56C、64C‧‧‧第三埠 56C, 64C‧‧‧third port
56D、64D‧‧‧第四埠 56D, 64D‧‧‧4th port
56E、64E‧‧‧第五埠 56E, 64E‧‧‧Port 5
64F‧‧‧導引埠 64F‧‧‧ Pilot port
66a至66e‧‧‧流路 66a to 66e‧‧‧flow path
68‧‧‧第二固定節流閥 68‧‧‧Second fixed throttle
70‧‧‧第二消音器 70‧‧‧Second silencer
72‧‧‧第一導引閥 72‧‧‧First pilot valve
74‧‧‧第二導引閥 74‧‧‧Second pilot valve
76A、80A‧‧‧第一埠 76A, 80A‧‧‧First port
76B、80B‧‧‧第二埠(供給埠) 76B, 80B‧‧‧Second port (supply port)
76C、80C‧‧‧第三埠 76C, 80C‧‧‧third port
76D、80D‧‧‧第四埠(連動埠) 76D, 80D‧‧‧Fourth port (connecting port)
78a‧‧‧流路 78a‧‧‧Flow Path
78b‧‧‧第一導引流路 78b‧‧‧First guide flow path
78c‧‧‧分岔流路 78c‧‧‧Branch flow path
82a‧‧‧流路 82a‧‧‧Flow Path
82b‧‧‧第二導引流路 82b‧‧‧Second guide flow path
82c‧‧‧分岔流路 82c‧‧‧Branch flow path
84‧‧‧閥收容孔 84‧‧‧Valve receiving hole
84a‧‧‧大徑孔部 84a‧‧‧Large diameter hole
84b‧‧‧小徑孔部 84b‧‧‧Small diameter hole
84c‧‧‧中徑孔部 84c‧‧‧Pitch hole
86‧‧‧閥座 86‧‧‧Valve seat
86a‧‧‧環狀溝 86a‧‧‧Annular groove
86b‧‧‧環狀凹部 86b‧‧‧Annular recess
86c‧‧‧第一貫通孔 86c‧‧‧First through hole
86d‧‧‧第二貫通孔 86d‧‧‧Second through hole
88‧‧‧閥座壓件 88‧‧‧Valve seat pressure piece
90‧‧‧控制銷 90‧‧‧Control pin
90a‧‧‧大徑軸部 90a‧‧‧Large diameter shaft
90b‧‧‧中徑軸部 90b‧‧‧Pitch diameter shaft
90c‧‧‧小徑軸部 90c‧‧‧Small diameter shaft
90d‧‧‧環狀溝 90d‧‧‧Annular groove
90e‧‧‧段差面 90e‧‧‧Segment difference
92‧‧‧固定環 92‧‧‧Fixed ring
94a‧‧‧第一密封件 94a‧‧‧First seal
94b‧‧‧第二密封件 94b‧‧‧Second seal
96a‧‧‧第三密封件 96a‧‧‧Third seal
96b‧‧‧第四密封件 96b‧‧‧Fourth seal
98a‧‧‧第一襯墊 98a‧‧‧First liner
98b‧‧‧第二襯墊 98b‧‧‧Second liner
98c‧‧‧第三襯墊 98c‧‧‧third liner
A1、A2‧‧‧方向 A1, A2‧‧‧direction
第1圖為本發明實施形態之增壓裝置的外觀立體圖。 Figure 1 is a perspective view of the appearance of a supercharging device according to an embodiment of the present invention.
第2圖為第1圖之增壓裝置的側視圖。 Figure 2 is a side view of the supercharging device of Figure 1.
第3圖為第2圖之III-III線的剖面圖。 Figure 3 is a cross-sectional view taken along the line III-III of Figure 2.
第4圖為第2圖之IV-IV線的剖面圖。 Figure 4 is a cross-sectional view taken along the line IV-IV in Figure 2.
第5圖為以流體迴路圖表示之第1圖的增壓裝置的整體概略圖。 Fig. 5 is an overall schematic diagram of the supercharging device of Fig. 1 shown in a fluid circuit diagram.
第6圖為第1圖增壓裝置之第一導引閥的剖面圖。 Figure 6 is a cross-sectional view of the first pilot valve of the pressurizing device of Figure 1.
第7圖為與第6圖對應之第一導引閥之控制銷移動到其他位置時的圖。 Figure 7 is a diagram when the control pin of the first pilot valve corresponding to Figure 6 moves to another position.
第8圖為與第6圖對應之第一導引閥之控制銷再移動到其他位置時的圖。 Figure 8 is a diagram when the control pin of the first pilot valve corresponding to Figure 6 is moved to another position.
第9圖為與第5圖對應之增壓裝置從第5圖的狀態變換到其他狀態時的圖。 Fig. 9 is a diagram when the supercharging device corresponding to Fig. 5 is changed from the state of Fig. 5 to another state.
以下,參照附圖,就本發明之增壓裝置例舉較佳實施形態詳加說明。本發明實施形態的增壓裝置10係配設在未圖示的壓力流體供給源(壓縮機)與藉由增壓後的壓力流體來動作的未圖示的致動器之間。
Hereinafter, with reference to the drawings, a detailed description will be given of the preferred embodiments of the supercharging device of the present invention. The supercharging
如第1圖及第3圖所示,增壓裝置10係具有在增壓用缸12的一端側(A1方向側)及另一端側(A2方向側)分別連設有第一驅動用缸14及第二驅動用缸16的三連式缸構造。亦即,增壓裝置10中,從A1方向朝向A2方向,依序連設有第一驅動用缸14、增壓用缸12及第二驅動用缸16。
As shown in Figures 1 and 3, the supercharging
第一驅動用缸14與增壓用缸12之間隔有塊狀的第一蓋構件18,增壓用缸12與第二驅動用缸16之間隔有塊狀的第二蓋構件20。
A block-shaped
增壓用缸12的內部形成有增壓室22,第一驅動用缸14及第二驅動用缸16的內部分別形成有第一驅動室24及第二驅動室26。此時,藉由在第一驅動用缸14之A1方向的端部固定第三蓋構件28,在A2方向的端部配設第一蓋構件18,即形成第一驅動室24。再者,藉由在第二驅動用缸16之A1方向的端部配設第二蓋構件20,且以壁部30封閉A2方向的端部,即形成第二驅動室26。
A
如第3圖所示,活塞桿32係配設成貫通第一蓋構件18、增壓用缸12及第二蓋構件20。活塞桿32的一端部係延伸到第一驅動室24,活塞桿32的另一端部則延伸到第二驅動室26。
As shown in FIG. 3, the
增壓室22中,在活塞桿32的中央部連結有增壓用活塞34。藉此,增壓室22被劃分成A1方向側的第一增壓室22a及A2方向側的第二增壓室22b(參照第5圖)。第一驅動室24中,在活塞桿32的一端部連結有第一驅動用活塞36。藉此,第一驅動室24被劃分成A1方向側的加壓室24a及A2方向側的背壓室24b(參照第5圖)。此外,第二驅動室26中,
在活塞桿32的另一端部連結有第二驅動用活塞38。藉此,第二驅動室26被劃分成A2方向側的加壓室26a及A1方向側的背壓室26b(參照第5圖)。增壓用活塞34、第一驅動用活塞36及第二驅動用活塞38係藉由活塞桿32一體地連結。
In the pressurizing
如第1圖所示,在增壓用缸12的前面上部,形成有從未圖示之壓力流體供給源接受壓力流體供給的供給埠40。如第4圖及第5圖所示,在增壓用缸12、第一蓋構件18及第二蓋構件20的內部,設有連通於供給埠40,將所供給的壓力流體供給到第一增壓室22a及第二增壓室22b的流體供給機構。流體供給機構係具有:第一供給流路42a,係連通供給埠40與第一增壓室22a;及第二供給流路42b,係連通供給埠40與第二增壓室22b。
As shown in FIG. 1, a
第一供給流路42a中設有容許流體從供給埠40向第一增壓室22a流動而阻止流體從第一增壓室22a向供給埠40流動的第一供給逆止閥42c。第二供給流路42b中設有容許流體從供給埠40向第二增壓室22b流動而阻止流體從第二增壓室22b向供給埠40流動的第二供給逆止閥42d。
The first
如第1圖所示,增壓用缸12的前面下部形成有將藉由後述的增壓動作而增壓的流體輸出到外部的輸出口44。如第4圖及第5圖所示,增壓用缸12、第一蓋構件18及第二蓋構件20的內部設有連通於輸出口44,且將經第一增壓室22a或第二增壓室22b增壓後的流體從輸出口44輸出的流體輸出機構。流體輸出機構具有:第一輸出流路46a,係連通第一增壓室22a與輸出口44;及第二輸出流路46b,係連通第二增壓室22b與輸出口44。
As shown in FIG. 1, an
第一輸出流路46a中設有容許流體從第一增壓室22a向輸出口44流動而阻止流體從輸出口44向第一增壓室22a流動的第一輸出逆止閥46c。第二輸出流路46b中設有容許流體從第二增壓室22b向輸出口44流動而阻止流體從輸出口44向第二增壓室22b流動的第二輸出逆止閥46d。
The first
接著,說明有關動作閥的構成。如第1圖所示,第一驅動用缸14的上部配設有具備第一動作閥48的第一殼體50,第二驅動用缸16的上部配設有具備第二動作閥52的第二殼體54。
Next, the structure of the operating valve will be described. As shown in Figure 1, the upper part of the
如第5圖所示,第一動作閥48係具有作為流路之連接、切換點的第一埠56A至第五埠56E,且構成為可在用以驅動第一驅動用活塞36的第一位置與用以使第一驅動用活塞36伴隨第二驅動用活塞38之驅動而動作的第二位置之間切換。
As shown in Fig. 5, the
第一埠56A係藉由流路58a連接於第一驅動用缸14的加壓室24a。第二埠56B係藉由流路58b連接於第一驅動用缸14的背壓室24b。第三埠56C係藉由流路58c連接於第一供給流路42a。第四埠56D係藉由流路58d連接於具備排出口的第一消音器62。第五埠56E係藉由流路58e連接於流路58a的中途。流路58d中係插裝有第一固定節流閥60。
The
第一動作閥48位於第一位置時,第一埠56A與第三埠56C相連通,並且,第二埠56B與第四埠56D相連通。藉此,來自供給埠40的壓力流體係通過流路58c及流路58a而供給到加壓室24a,背壓室24b的流體則通過流路58b及流路58d而經由第一固定節流閥60及第一消音器62排出。
When the
第一動作閥48位於第二位置時,第一埠56A與第四埠56D相連通,並且,第二埠56B與第五埠56E相連通。藉此,加壓室24a之流
體的一部分係通過流路58a、流路58e及流路58b而回收到背壓室24b,其餘則通過流路58d而經由第一固定節流閥60及第一消音器62排出。
When the
第一動作閥48還具有用以從後述第二導引閥74導入導引壓力的導引埠56F。第一動作閥48係在壓力流體(導引壓力)供給到導引埠56F時位於第一位置,而在壓力流體(導引壓力)未供給到導引埠56F時位於第二位置。
The
第二動作閥52係具有作為流路之連接、切換點的第一埠64A至第五埠64E,且構成為可在用以驅動第二驅動用活塞38的第一位置與用以使第二驅動用活塞38伴隨第一驅動用活塞36之驅動而動作的第二位置之間切換。
The
第一埠64A係藉由流路66a連接於第二驅動用缸16的加壓室26a。第二埠64B係藉由流路66b連接於第二驅動用缸16的背壓室26b。第三埠64C係藉由流路66c連接於第二供給流路42b。第四埠64D係藉由流路66d連接於具備排出口的第二消音器70。第五埠64E係藉由流路66e連接於流路66a的中途。流路66d中係插裝有第二固定節流閥68。
The
第二動作閥52位於第一位置時,第一埠64A與第三埠64C相連通,並且,第二埠64B與第四埠64D相連通。藉此,來自供給埠40的壓力流體係通過流路66c及流路66a而供給到加壓室26a,背壓室26b的流體則通過流路66b及流路66d而經由第二固定節流閥68及第二消音器70排出。
When the
第二動作閥52位於第二位置時,第一埠64A與第四埠64D相連通,並且,第二埠64B與第五埠64E相連通。藉此,加壓室26a之流體的一部分係通過流路66a、流路66e及流路66b而回收到背壓室26b,其餘則通過流路66d而經由第二固定節流閥68及第二消音器70排出。
When the
第二動作閥52還具有用以從後述的第一導引閥72導入導引壓力的導引埠64F。第二動作閥52係在壓力流體(導引壓力)供給到導引埠64F時位於第一位置,而在壓力流體(導引壓力)未供給到導引埠64F時位於第二位置。
The
接著說明有關導引閥的構成。第一蓋構件18的內部配設有第一導引閥72,第二蓋構件20的內部配設有第二導引閥74。
Next, the structure of the pilot valve will be explained. A
第一導引閥72係具有第一埠76A至第四埠76D,且構成為可在用以對第二動作閥52產生導引壓力的第一位置與用以使該導引壓力消除的第二位置之間切換。
The
第一埠76A係藉由第一導引流路78b連接於第二動作閥52的導引埠64F。第二埠(供給埠)76B係藉由流路78a連接於第一供給流路42a。第三埠76C係構成排出口。第四埠(連動埠)76D係藉由後述的分岔流路82c及第二導引流路82b連接於後述第二導引閥74之第一埠80A。此外,到達後述第二導引閥74之第四埠80D的分岔流路78c係自第一導引流路78b分岔設置。
The
第一導引閥72位於第一位置時,第一埠76A與第二埠76B相連通。藉此,來自供給埠40的壓力流體係通過流路78a及第一導引流路78b而供給到第二動作閥52的導引埠64F,並且通過從第一導引流路78b分岔的分岔流路78c而供給到後述第二導引閥74的第四埠80D。
When the
第一導引閥72位於第二位置時,第一埠76A與第三埠76C相連通。藉此,供給到第二動作閥52之導引埠64F的壓力流體係通過第一導引流路78b被排出,並且,供給到第二導引閥74之第四埠80D的壓力流體係通過分岔流路78c及第一導引流路78b而被排出。
When the
第二導引閥74係具有第一埠80A至第四埠80D,且構成為可在用以對第一動作閥48產生導引壓力的第一位置與用以使該導引壓力消除的第二位置之間切換。
The
第一埠80A係藉由第二導引流路82b連接於第一動作閥48的導引埠56F。第二埠(供給埠)80B係藉由流路82a連接於第二供給流路42b。第三埠80C係構成排出口。第四埠80D(連動埠)係藉由分岔流路78c及第一導引流路78b連接於第一導引閥72的第一埠76A。此外,到達第一導引閥72之第四埠76D的分岔流路82c係自第二導引流路82b分岔設置。
The
第二導引閥74位於第一位置時,第一埠80A與第二埠80B相連通。藉此,來自供給埠40的壓力流體係通過流路82a及第二導引流路82b而供給到第一動作閥48的導引埠56F,並且通過自第二導引流路82b分岔的分岔流路82c而供給到第一導引閥72的第四埠76D。
When the
第二導引閥74位於第二位置時,第一埠80A與第三埠80C相連通。藉此,供給到第一動作閥48之導引埠56F的壓力流體係通過第二導引流路82b被排出,並且,供給到第一導引閥72之第四埠76D的壓力流體係通過分岔流路82c及第二導引流路82b而被排出。
When the
在此,參照第6圖至第8圖,就第一導引閥72的具體構造加以說明。另外,關於第二導引閥74的具體構造,因與第一導引閥72相同,故其說明從略。
Here, referring to FIGS. 6 to 8, the specific structure of the
第一導引閥72係包括收容於第一蓋構件18所設的閥收容孔84的閥座86、閥座壓件88及控制銷90。閥收容孔84係增壓用缸12側封閉,第一驅動用缸14側開放。閥收容孔84的封閉側端部係成為大徑孔部84a,第四埠76D係與此大徑孔部84a連通。
The
閥收容孔84係具有銜接於大徑孔部84a的小徑孔部84b及銜接於小徑孔部84b之開口側的中徑孔部84c。第一埠76A、第二埠76B及第三埠76C係與閥收容孔84的小徑孔部84b連通。此等三個埠之中,第二埠76B係位於最接近第四埠76D的位置,第三埠76C係位於距離第四埠76D最遠的位置。
The valve
薄壁圓筒狀的閥座86及厚壁圓筒狀的閥座壓件88係嵌設於閥收容孔84的小徑孔部84b。閥座壓件88係軸向一端面對向第一驅動用缸14的背壓室24b,而軸向另一端面抵接於閥座86。在閥收容孔84的中徑孔部84c固定有抵接於閥座壓件88的固定環92。藉此,將閥座86及閥座壓件88軸向定位並固定在閥收容孔84內。另外,閥座86係卡止在設於小徑孔部84b中途的段差部。
The thin-walled
在閥座86之軸向中央部的外周設有與第一埠76A相對的環狀溝86a,在閥座壓件88抵接側的閥座86之軸向端部的外周設有與第三埠76C相對的環狀凹部86b。閥座86的環狀溝86a係經由徑向貫穿閥座86的第一貫通孔86c而連通於閥座86的內周側,閥座86之環狀凹部86b係經由徑向貫穿閥座86的第二貫通孔86d而連通於閥座86的內周側。
An
在閥座86的外周面,藉由溝部分別裝設有抵接於閥收容孔84之小徑孔部84b的第一密封件94a及第二密封件94b。第一密封件94a係介於閥座86與閥收容孔84間的間隙而阻止第一埠76A與第二埠76B連通,第二密封件94b係介於閥座86與閥收容孔84間的間隙而阻止第一埠76A與第三埠76C連通。
On the outer peripheral surface of the
在閥座壓件88的外周面,藉由溝部裝設有抵接於閥收容孔84之小徑孔部84b的第三密封件96a,在閥座壓件88的內周面,藉由溝部裝設有滑接於控制銷90的第四密封件96b。藉由第三密封件96a及第四
密封件96b,第三埠76C與第一驅動用缸14的背壓室24b之間即獲得密封。
On the outer peripheral surface of the valve
控制銷90係具有大徑軸部90a、中徑軸部90b及小徑軸部90c。大徑軸部90a係嵌插於閥收容孔84的小徑孔部84b。中徑軸部90b係以一部分從閥座86突出的狀態嵌插於閥座86的內側,而從閥座86突出的部分則徑向隔著預定間隙而與閥收容孔84的小徑孔部84b相對。小徑軸部90c係嵌插於閥座壓件88的內側。
The
控制銷90的大徑軸部90a中,藉由溝部裝設有滑接於閥收容孔84之小徑孔部84b的第一襯墊98a。第一襯墊98a係用以將第二埠76B與第四埠76D之間密封。控制銷90的中徑軸部90b中,藉由溝部裝設有可滑接於閥座86之內周面的第二襯墊98b及第三襯墊98c。控制銷90之中徑軸部90b的外周,在第二襯墊98b的裝設部位與第三襯墊98c的裝設部位之間設有環狀溝90d。
In the large-
控制銷90可滑動於大徑軸部90a側之端部抵接於閥收容孔84之底面(封閉端面)的位置,以及中徑軸部90b與小徑軸部90c間的段差面90e抵接於閥座壓件88之端面的位置之間。控制銷90抵接於閥座壓件88的端面時,控制銷90的小徑軸部90c突出第一驅動用缸14之背壓室24b內的長度(以下稱為「控制銷的突出長度」)係達到最大。第一驅動用活塞36可抵接於控制銷90之小徑軸部90c側端部,將控制銷90推壓向閥收容孔84的底面側。
The
不論控制銷90的突出長度如何,控制銷90的環狀溝90d均經由閥座86的第一貫通孔86c而連通於環狀溝86a。換言之,控制銷90的環狀溝90d係恆常地連通於第一埠76A,而與控制銷90的位置無關。再
者,第二埠76B係恆常地連通於形成在控制銷90之中徑軸部90b與閥收容孔84之小徑孔部84b之間的間隙。
Regardless of the protruding length of the
控制銷90的突出長度大時,第二襯墊98b係抵接於閥座86的內面,並且第三襯墊98c係離開閥座86的內面(參照第6圖)。因此,第一埠76A係經由包含控制銷90的環狀溝90d的控制銷90與閥座86之內面間的間隙、閥座86的第二貫通孔86d及環狀凹部86b而連通於第三埠76C。
When the protruding length of the
第一驅動用活塞36抵接於控制銷90使得控制銷90的突出長度較上述稍微減少時,第二襯墊98b及第三襯墊98c的任一者皆抵接於閥座86的內面(參照第7圖)。因此,第一埠76A不會連通於第二埠76B及第三埠76C的任一者。
When the
控制銷90的突出長度小時,第二襯墊98b係離開閥座86的內面,並且第三襯墊98c係抵接於閥座86的內面(參照第8圖)。因此,第一埠76A可經由包含控制銷90的環狀溝90d的控制銷90與閥座86之內面間的間隙、以及控制銷90之中徑軸部90b與閥收容孔84之小徑孔部84b間所形成的間隙而連通於第二埠76B。
When the protruding length of the
對第四埠76D供給壓力流體時,控制銷90係朝向突出長度增大的方向被推壓。其理由是因朝向使控制銷90之突出長度增大的方向施加的第四埠76D之流體壓力的作用面積(受壓面積)係大於朝向使控制銷90的突出長度減少之方向施加的第二埠76B之流體壓力的作用面積(受壓面積)。
When the pressure fluid is supplied to the
另一方面,不對第四埠76D供給壓力流體時,控制銷90係朝向突出長度減少的方向被推壓。其理由是因朝向使控制銷90之突出長度
增大的方向施加的第四埠76D之流體壓力消失,而朝向使控制銷90的突出長度減少的方向施加的第二埠76B之流體壓力受到維持。
On the other hand, when the pressure fluid is not supplied to the
本發明第1實施形態的增壓裝置10基本上係如以上地構成,接著針對其動作及作用效果加以說明。如第5圖所示,以第一動作閥48處於切換到第二位置的狀態且第二動作閥52處於切換到第一位置的狀態,並且,增壓用活塞34位於靠增壓室22中央的狀態作為初始位置。另外,以下的說明中,為了區別第一導引閥72的控制銷與第二導引閥74的控制銷,將前者稱為「控制銷90-1」,後者稱為「控制銷90-2」。再者,為了區別第一導引閥72的閥收容孔與第二導引閥74的閥收容孔,將前者稱為「閥收容孔84-1」,後者稱為「閥收容孔84-2」。
The supercharging
此初始位置中,藉由從壓力流體供給源朝供給埠40供給壓力流體,使壓力流體流入第一供給流路42a及第二供給流路42b。然後,經由第一供給逆止閥42c及第二供給逆止閥42d而導入增壓用缸12的第一增壓室22a及第二增壓室22b。
In this initial position, by supplying the pressure fluid from the pressure fluid supply source to the
從供給埠40供給之壓力流體的一部分係通過流路66c、位於第一位置的第二動作閥52、及流路66a而供給到第二驅動用缸16的加壓室26a。藉由供給到此加壓室26a的壓力流體使第二驅動用活塞38朝A1方向驅動。藉此,與第二驅動用活塞38一體地連結的增壓用活塞34滑動,使增壓用缸12之第一增壓室22a的壓力流體獲得增壓。經增壓的壓力流體係通過第一輸出流路46a及第一輸出逆止閥46c導向輸出口44而輸出。
A part of the pressure fluid supplied from the
另一方面,與第二驅動用活塞38一體地連結的第一驅動用活塞36滑動時,第一驅動用缸14之加壓室24a的容積變小。因第一動作
閥48位於第二位置,故加壓室24a內的壓力流體的一部分係通過流路58a、流路58e及流路58b而回收到背壓室24b,其餘則通過流路58d排出。
On the other hand, when the
如上所述,增壓用活塞34從初始位置朝向A1方向移動預定距離的行程中,第一導引閥72係位於第一位置,來自供給埠40的壓力流體係經由第一導引閥72而供給到第二導引閥74的第四埠80D。另一方面,第二導引閥74係位於第二位置,壓力流體不會供給到第一導引閥72的第四埠76D。因此,第一導引閥72中,朝向控制銷90-1之突出長度減少的方向推壓,第一導引閥72係穩定地保持在第一位置。再者,第二導引閥74中,朝向控制銷90-2之突出長度增大的方向推壓,第二導引閥74係穩定地保持在第二位置。
As described above, in the stroke of the
然後,如第9圖所示,在增壓用活塞34朝A1方向位移的行程終點附近,第二驅動用活塞38係抵接於第二導引閥74的控制銷90-2。控制銷90-2受到第二驅動用活塞38的推壓而位移到第二導引閥74的第一埠80A與第二埠80B相連通。於是,來自供給埠40的壓力流體係通過第二導引流路82b供給到第一動作閥48的導引埠56F,並且經由分岔流路82c供給到第一導引閥72的第四埠76D。藉此,第一動作閥48係切換到第一位置,並且第一導引閥72係切換到第二位置。
Then, as shown in FIG. 9, the
第一導引閥72切換到第二位置時,供給到第二動作閥52之導引埠64F的壓力流體係通過第一導引流路78b而從第一導引閥72的第三埠76C被排出。藉此,第二動作閥52係切換到第二位置。
When the
其次,第一導引閥72切換到第二位置時,供給到第二導引閥74之第四埠80D的壓力流體係通過分岔流路78c及第一導引流路78b而從第一導引閥72的第三埠76C被排出。因此,第二導引閥74中,流體壓力係朝向使控制銷90-2的突出長度減少的方向作用。依此,藉由第二驅
動用活塞38的推壓而位移到使第二導引閥74的第一埠80A與第二埠80B相連通的控制銷90-2係更承受流體壓力而保持在抵接於閥收容孔84-2之底面的位置。亦即,第二導引閥74係穩定地保持在第一位置。此第二導引閥74保持於第一位置的狀態係如後述地維持到第一驅動用活塞36朝向A2方向被驅動而使控制銷90-1位移時為止。
Next, when the
接下來,從供給埠40供給的壓力流體的一部分係通過流路58c、位於第一位置的第一動作閥48及流路58a而供給到第一驅動用缸14的加壓室24a。藉由供給到此加壓室24a的壓力流體使第一驅動用活塞36朝向A2方向驅動。藉此,與第一驅動用活塞36一體地連結的增壓用活塞34滑動,使增壓用缸12之第二增壓室22b的壓力流體獲得增壓。經增壓的壓力流體係通過第二輸出流路46b及第二輸出逆止閥46d導向輸出口44而輸出。
Next, a part of the pressure fluid supplied from the
另一方面,與第一驅動用活塞36一體地連結的第二驅動用活塞38滑動時,第二驅動用缸16之加壓室26a的容積變小。因第二動作閥52位於第二位置,故加壓室26a內的壓力流體的一部分係通過流路66a、流路66e及流路66b而回收到背壓室26b,其餘部分則通過流路66d排出。
On the other hand, when the
然後,在增壓用活塞34朝向A2方向位移的行程終點附近,第一驅動用活塞36係抵接於第一導引閥72的控制銷90-1。控制銷90-1受到第一驅動用活塞36的推壓而位移到第一導引閥72的第一埠76A與第二埠76B相連通。於是,來自供給埠40的壓力流體係通過第一導引流路78b供給到第二動作閥52的導引埠64F,並且通過分岔流路78c供給到第二導引閥74的第四埠80D。藉此,第二動作閥52係切換到第一位置,並且第二導引閥74係切換到第二位置。
Then, in the vicinity of the stroke end point at which the
第二導引閥74切換到第二位置時,供給到第一動作閥48之導引埠56F的壓力流體係通過第二導引流路82b而從第二導引閥74的第三埠80C被排出。藉此,第一動作閥48係切換到第二位置。
When the
再者,第二導引閥74切換到第二位置時,供給到第一導引閥72之第四埠76D的壓力流體係通過分岔流路82c及第二導引流路82b而從第二導引閥74的第三埠80C被排出。因此,第一導引閥72中,流體壓力係朝向使控制銷90-1的突出長度減少的方向作用。依此,藉由第一驅動用活塞36的推壓而位移到使第一導引閥72之第一埠76A與第二埠76B相連通的控制銷90-1係更承受流體壓力而保持在抵接於閥收容孔84-1之底面的位置。亦即,第一導引閥72係穩定地保持在第一位置。此第一導引閥72保持於第一位置之狀態係維持到第二驅動用活塞38再度朝向A1方向被驅動而使控制銷90-2位移為止。以下,增壓用活塞34係同樣地反覆進行往返運動,從輸出口44連續地輸出增壓後的壓力流體。
Furthermore, when the
若依據本實施形態的增壓裝置10,藉由第一驅動用活塞36的推壓而位移到第一導引閥72之第一埠76A與第二埠76B相連通的控制銷90-1可進一步藉由預定的流體壓力推入到與閥收容孔84-1的底面抵接的位置為止,且保持在其位置。同樣地,藉由第二驅動用活塞38的推壓而位移到第二導引閥74之第一埠80A與第二埠80B相連通的控制銷90-2亦可進一步藉預定的流體壓力推入到與閥收容孔84-2的底面抵接的位置為止,且保持在其位置。
According to the pressurizing
再者,第一動作閥48係從與第一導引閥72連動而切換位置的第二導引閥74供給導引壓力時切換到第一位置,未從第二導引閥74供給導引壓力時則切換到第二位置。同樣地,第二動作閥52係從與第二導引閥74連動而切換位置的第一導引閥72供給導引壓力時切換到第一位置,
未從第一導引閥72供給導引壓力時則切換到第二位置。因此,第一動作閥48及第二動作閥52可穩定地動作,同時進行切換。
Furthermore, the
再者,由於將驅動第一驅動用活塞36之際供給到加壓室24a之流體的一部分,在伴隨第二驅動用活塞38之驅動使第一驅動用活塞36跟隨之際,回收到背壓室24b,故可減少壓力流體的消耗量。同樣地,由於將驅動第二驅動用活塞38之際供給到加壓室26a之流體的一部分,在伴隨第一驅動用活塞36之驅動使第二驅動用活塞38跟隨之際,回收到背壓室26b,故可減少壓力流體的消耗量。
Furthermore, since part of the fluid supplied to the pressurizing
本發明的增壓裝置不限於上述實施形態,在不逸離本發明要旨的範圍內,當然可採用各種構成。 The supercharging device of the present invention is not limited to the above-mentioned embodiment, and of course various configurations can be adopted within the scope not departing from the gist of the present invention.
10‧‧‧增壓裝置 10‧‧‧Boosting device
12‧‧‧增壓用缸 12‧‧‧Pressurized cylinder
14‧‧‧第一驅動用缸 14‧‧‧The first drive cylinder
16‧‧‧第二驅動用缸 16‧‧‧Second drive cylinder
22‧‧‧增壓室 22‧‧‧Pressure chamber
22a‧‧‧第一增壓室 22a‧‧‧First pressurization chamber
22b‧‧‧第二增壓室 22b‧‧‧Second plenum
24‧‧‧第一驅動室 24‧‧‧First Drive Room
26‧‧‧第二驅動室 26‧‧‧Second Drive Room
24a、26a‧‧‧加壓室 24a、26a‧‧‧Pressure chamber
24b、26b‧‧‧背壓室 24b, 26b‧‧‧Back pressure chamber
32‧‧‧活塞桿 32‧‧‧Piston rod
34‧‧‧增壓用活塞 34‧‧‧Piston for pressurization
36‧‧‧第一驅動用活塞 36‧‧‧Piston for the first drive
38‧‧‧第二驅動用活塞 38‧‧‧Second drive piston
40‧‧‧供給埠 40‧‧‧Supply Port
42a‧‧‧第一供給流路 42a‧‧‧First supply flow path
42b‧‧‧第二供給流路 42b‧‧‧Second supply flow path
42c‧‧‧第一供給逆止閥 42c‧‧‧First supply check valve
42d‧‧‧第二供給逆止閥 42d‧‧‧Second supply check valve
44‧‧‧輸出口 44‧‧‧Output port
46a‧‧‧第一輸出流路 46a‧‧‧First output channel
46b‧‧‧第二輸出流路 46b‧‧‧Second output channel
46c‧‧‧第一輸出逆止閥 46c‧‧‧First output check valve
46d‧‧‧第二輸出逆止閥 46d‧‧‧Second output check valve
48‧‧‧第一動作閥 48‧‧‧First action valve
52‧‧‧第二動作閥 52‧‧‧Second action valve
56F‧‧‧導引埠 56F‧‧‧ Pilot port
58a至58e‧‧‧流路 58a to 58e‧‧‧Flow path
60‧‧‧第一固定節流閥 60‧‧‧The first fixed throttle
62‧‧‧第一消音器 62‧‧‧First silencer
56A、64A‧‧‧第一埠 56A, 64A‧‧‧First port
56B、64B‧‧‧第二埠 56B, 64B‧‧‧Second port
56C、64C‧‧‧第三埠 56C, 64C‧‧‧third port
56D、64D‧‧‧第四埠 56D, 64D‧‧‧4th port
56E、64E‧‧‧第五埠 56E, 64E‧‧‧Port 5
64F‧‧‧導引埠 64F‧‧‧ Pilot port
66a至66e‧‧‧流路 66a to 66e‧‧‧flow path
68‧‧‧第二固定節流閥 68‧‧‧Second fixed throttle
70‧‧‧第二消音器 70‧‧‧Second silencer
72‧‧‧第一導引閥 72‧‧‧First pilot valve
74‧‧‧第二導引閥 74‧‧‧Second pilot valve
76A、80A‧‧‧第一埠 76A, 80A‧‧‧First port
76B、80B‧‧‧第二埠(供給埠) 76B, 80B‧‧‧Second port (supply port)
76C、80C‧‧‧第三埠 76C, 80C‧‧‧third port
76D、80D‧‧‧第四埠(連動埠) 76D, 80D‧‧‧Fourth port (connecting port)
78a‧‧‧流路 78a‧‧‧Flow Path
78b‧‧‧第一導引流路 78b‧‧‧First guide flow path
78c‧‧‧分岔流路 78c‧‧‧Branch flow path
82a‧‧‧流路 82a‧‧‧Flow Path
82b‧‧‧第二導引流路 82b‧‧‧Second guide flow path
82c‧‧‧分岔流路 82c‧‧‧Branch flow path
90‧‧‧控制銷 90‧‧‧Control pin
A1、A2‧‧‧方向 A1, A2‧‧‧direction
Claims (5)
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JP (1) | JP7314463B2 (en) |
KR (1) | KR102523626B1 (en) |
CN (1) | CN112567140B (en) |
BR (1) | BR112021002800A2 (en) |
MX (1) | MX2021001767A (en) |
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CN113374745B (en) * | 2021-07-06 | 2022-05-20 | 中煤科工集团重庆研究院有限公司 | Hydraulic system for continuously conveying drill rods |
CN113404731B (en) * | 2021-07-06 | 2022-05-20 | 中煤科工集团重庆研究院有限公司 | Synchronous continuous conveying drill rod hydraulic system with locking function |
CN113374744B (en) * | 2021-07-06 | 2022-05-06 | 中煤科工集团重庆研究院有限公司 | Continuous conveying drill rod hydraulic system with locking function |
CN113374746B (en) * | 2021-07-06 | 2022-05-20 | 中煤科工集团重庆研究院有限公司 | Synchronous continuous conveying drill rod hydraulic system |
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2019
- 2019-07-24 CN CN201980053314.9A patent/CN112567140B/en active Active
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- 2019-07-24 WO PCT/JP2019/028933 patent/WO2020036046A1/en unknown
- 2019-07-24 BR BR112021002800-5A patent/BR112021002800A2/en not_active IP Right Cessation
- 2019-07-24 KR KR1020217006954A patent/KR102523626B1/en active IP Right Grant
- 2019-07-24 MX MX2021001767A patent/MX2021001767A/en unknown
- 2019-07-24 EP EP19849370.2A patent/EP3839265A4/en active Pending
- 2019-08-15 TW TW108129127A patent/TWI704292B/en active
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
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US2296647A (en) * | 1941-02-28 | 1942-09-22 | Racine Tool & Machine Company | Hydraulic pressure booster |
JPS4033392Y1 (en) * | 1965-07-23 | 1965-11-22 | ||
JP4033392B2 (en) | 2003-03-19 | 2008-01-16 | 株式会社リコー | Image forming apparatus |
TWM452245U (en) * | 2012-12-28 | 2013-05-01 | Kinyao Entpr Co Ltd | Hydraulic booster pump structure |
TWI595159B (en) * | 2014-12-31 | 2017-08-11 | High-pressure cylinder and booster system | |
TW201819777A (en) * | 2016-11-22 | 2018-06-01 | 日商Smc股份有限公司 | Pressure booster |
Also Published As
Publication number | Publication date |
---|---|
WO2020036046A1 (en) | 2020-02-20 |
EP3839265A1 (en) | 2021-06-23 |
KR20210040136A (en) | 2021-04-12 |
CN112567140A (en) | 2021-03-26 |
BR112021002800A2 (en) | 2021-05-04 |
MX2021001767A (en) | 2021-04-19 |
EP3839265A4 (en) | 2022-04-20 |
TW202016436A (en) | 2020-05-01 |
JPWO2020036046A1 (en) | 2021-08-26 |
KR102523626B1 (en) | 2023-04-19 |
CN112567140B (en) | 2023-01-24 |
JP7314463B2 (en) | 2023-07-26 |
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