WO1997033109A1 - Clapet anti-retour - Google Patents

Clapet anti-retour Download PDF

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Publication number
WO1997033109A1
WO1997033109A1 PCT/JP1997/000723 JP9700723W WO9733109A1 WO 1997033109 A1 WO1997033109 A1 WO 1997033109A1 JP 9700723 W JP9700723 W JP 9700723W WO 9733109 A1 WO9733109 A1 WO 9733109A1
Authority
WO
WIPO (PCT)
Prior art keywords
port
chamber
check valve
valve
pressure
Prior art date
Application number
PCT/JP1997/000723
Other languages
English (en)
Japanese (ja)
Inventor
Mitsuru Oshiro
Original Assignee
Komatsu Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Komatsu Ltd. filed Critical Komatsu Ltd.
Publication of WO1997033109A1 publication Critical patent/WO1997033109A1/fr

Links

Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/08—Superstructures; Supports for superstructures
    • E02F9/10—Supports for movable superstructures mounted on travelling or walking gears or on other superstructures
    • E02F9/12—Slewing or traversing gears
    • E02F9/121—Turntables, i.e. structure rotatable about 360°
    • E02F9/123—Drives or control devices specially adapted therefor
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/08—Superstructures; Supports for superstructures
    • E02F9/10—Supports for movable superstructures mounted on travelling or walking gears or on other superstructures
    • E02F9/12—Slewing or traversing gears
    • E02F9/121—Turntables, i.e. structure rotatable about 360°
    • E02F9/128—Braking systems
    • 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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • 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
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40507—Flow control characterised by the type of flow control means or valve with constant throttles or orifices
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief valves
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5153—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve
    • F15B2211/5154—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve being connected to multiple ports of an output member
    • 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
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief valve
    • 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
    • F15B2211/7058—Rotary output members

Definitions

  • the present invention relates to a check valve used for a shuttle valve or the like that introduces high pressure to a safety valve provided in a Shantou pressure circuit that supplies hydraulic pressure discharged from a hydraulic pump to a hydraulic motor.
  • a hydraulic circuit for supplying hydraulic pressure discharged from a hydraulic pump to a hydraulic motor for example, a hydraulic circuit disclosed in Japanese Utility Model Laid-Open No. 52-77034 is known.
  • a hydraulic pump 1 is connected to both a first main circuit 3 and a second main circuit 4 via an operation valve 2, and the first main circuit 3 is connected to a hydraulic motor 5.
  • the second main circuit 4 was connected to the second port 7 of the hydraulic motor 5, and the discharge pressure oil of the hydraulic pump 1 was supplied to one of the first main circuit 3 and the second main circuit. To be supplied.
  • first main circuit 3 and the second main circuit 4 are connected to a high-pressure valve of a safety valve 10 via a first check valve 8 and a second check valve 9, respectively.
  • 10 is connected to the first main circuit 3 and the second main circuit 4 via the third check valve 11 and the fourth check valve 12, respectively.
  • the X check valve 8 and the second check valve 9 constitute a shuttle valve 13 for introducing high pressure to the safety valve 10. Then, with the operating valve 2 being in the first position A and supplying pressure to the first main circuit 3 to rotate the hydraulic motor 5 in one direction, the operating valve 2 is in the neutral position B. Then, when the hydraulic motor 5 rotates resentfully and performs a pump action, the pressure in the second main circuit 4 increases.
  • the pressure of the second main circuit 4 ⁇ flows from the second check valve 9 to the high pressure side of the safety valve 10, and the safety valve 10 is relieved. Since it flows into the first main circuit 3 via the three check valve 11, the hydraulic motor 5 can be stopped by braking. Similarly, when the operation valve 2 is switched from the neutral position B to the first position A to supply the discharge pressure oil of the hydraulic pump 1 to the first main circuit 3 and start the pressure oil motor 5, the safety valve 10 is also reset. Leaf operates to prevent abnormal high pressure in the first main circuit 3.
  • the safety valve 10 used in the hydraulic circuit described above uses a modulating safety valve that modulates the pressure rise gradient to reduce shocks when starting and stopping. are doing.
  • the safety valve 10 that increases in pressure in a short time to the modulation start pressure P1 and then gradually increases in pressure to the relief pressure P2 is activated. Used.
  • the conventional chinic valve allows the flow of pressure oil when the pressure oil flows in one direction, and instantaneously stops the flow of the pressure oil when the pressure oil flows in the other direction.
  • the first check valve 8 and the second check valve are used.
  • the shut-off valve 9 is constituted by the shut-off valve 9
  • confinement pressure is generated.
  • the first main circuit 3 is at high pressure and the second main circuit 4 is at low pressure
  • high-pressure oil is flowing between the first check valve 8 and the second check valve 9, and in this state
  • the second main circuit 4 becomes high pressure and the first main circuit 3 becomes low pressure
  • high-pressure oil between the first check valve 8 and the second check valve 9 flows out to the first main circuit 3 at all.
  • confinement pressure is generated as shown by diagonal lines in Fig. 3.
  • the modulating safety valve when using the modulating safety valve, the modulating safety valve must be connected to each of the first main circuit 3 and the second main circuit 4, so that two modulating safety valves are required.
  • the need for a safety valve increases the cost.
  • an object of the present invention is to provide a check valve which can solve the above-mentioned problem. Disclosure of the invention
  • one embodiment of a check valve according to the present invention allows a unidirectional pressurized oil flow from a first port to a second port and allows the first port to flow from the second port to the first port. Prevent the other direction of pressure flow to the port Main check valve and
  • the second port is provided more than the main check valve. Closer pressure decreases.
  • the leak check valve is
  • It has a first chamber and a second chamber, which are defined by installing free piston in the cylinder.
  • the first chamber communicates with the first port side
  • the second chamber communicates with the second port side
  • the free chamber cuts off the connection between the first chamber and the first port.
  • a passage communicating the first chamber and the second chamber may be formed in the free piston.
  • a discharge path of a hydraulic pump is connected to a first main circuit and a second main circuit via an operation valve, and the first main circuit and the second main circuit are connected to the i-th port and the second port of a hydraulic oil motor.
  • the first ports of the two check valves are respectively connected to the first main circuit and the second main circuit, and the second ports of the two check valves are connected to each other. Make up the valve,
  • the closing pressure in the shuttle valve is reduced, so that a sufficient modulation effect can be obtained by using one modulation safety valve. Shock during starting and stopping of the hydraulic motor can be reduced by one safety valve. The cost is also reduced.
  • Figure 1 is a hydraulic circuit diagram of a hydraulic motor.
  • FIG. 2 is a chart showing the operating characteristics of the modulation safety valve.
  • FIG. 3 is a chart showing pressure changes at various parts in a hydraulic circuit diagram of a conventional hydraulic motor.
  • FIG. 4 is an explanatory view showing a first embodiment of the check valve according to the present invention.
  • FIG. 5 is a hydraulic circuit diagram of a hydraulic motor using the first embodiment.
  • FIG. 6 is a sectional view showing a specific structure of the first embodiment.
  • FIG. 7 is a sectional view showing a state where the first embodiment is incorporated in a hydraulic motor.
  • FIG. 8 is an explanatory view showing a second embodiment of the check valve according to the present invention.
  • Check valve D is composed of 26.
  • the main check valve portion 23 allows the flow from the first port 20 to the second port 21 and prevents the flow from the second port 21 to the first port 20. .
  • the leak check valve portion 25 has a first chamber 29 and a second chamber 30 formed by inserting a free biston 28 into a cylinder 27, and forming the first chamber 2.
  • 9 communicates with the first port 20 side of the passage 24 through the port 3 1, forms a valve seat 32 on one inner surface of one end of the cylinder 27, and the valve element is connected to the free spring 28.
  • 33 is provided, and the second chamber 30 communicates with the second port 21 side of the passage 24 by the port 34.
  • the free piston 28 is provided with a passage 35 communicating between the first chamber 29 and the second chamber 30.
  • Pressurized oil flows from the first port 20 to the second port 21 via the main check valve 23 via the main passage 22. At the same time, the pressurized oil flows into the first chamber 29 via the throttle 26 on the right side of the passage 24 and moves to the left through the free piston 28, and the pressurized oil flows into the passage 24. 35, the second chamber 30 and the second port through the left throttle 26 in the passage 24. Flow to 2 1.
  • the pressurized oil flows from the first port 20 to the second port 21, the pressurized oil flows through the main check valve part 23, and the leak check valve part 25 is free.
  • the serviceton 28 moves leftward to the stroke, and the volume of the first room 29 becomes maximum and the volume of the second room 30 becomes minimum.
  • the main check valve 23 closes instantaneously in response to no pressure flow, but the second port 21 has a high pressure and the first port 20 has a low pressure.
  • the pressure in the second chamber 30 of the leaky piston 28 becomes higher than the pressure in the first chamber 29, and the flip ston 28 moves to the right to reduce the volume of the second chamber 30. Large and the volume of the i-th room 29 becomes small.
  • valve body 33 presses against the valve seat 32 and the first chamber 29 and the port 31 are pressed. Is shut off.
  • the check valve D of the present invention is combined as a pair to form a shuttle valve 13, and a circuit 36 connecting the pair of check valves D is provided with a safety valve 10.
  • the first main circuit 3 is connected to
  • the second main circuit 4 switches from the state to the high pressure state, part of the pressure remaining in the circuit 36 is relieved to the first main circuit 3 and the pressure in the second main circuit 4 decreases. I do.
  • the closing pressure becomes low, so that sufficient performance can be obtained when using the modular safety valve, and the shock at the time of starting and stopping can be reduced. it can.
  • a port 43 is inserted into a sleeve 42 screwed into a screw hole 41 of the housing 40, and the port 43 is attached by a spring 44. Push and crimp the conical valve part 45 to the valve seat 46 to shut off the ports 47 and 48.
  • the port 43 is moved to the left against the spring 44 by the pressure oil flowing into the port 47 to communicate the port 47 with the port 48, and
  • a blind hole 49 is formed in the port 43, a free piston 50 is inserted into the blind hole 49, and the blind hole 49 is closed by the cap 51.
  • a first chamber 52 and a second chamber 53 are formed.
  • the free piston 50 has a valve section
  • a passage 57 connecting the first chamber 52 to the second chamber 53 is formed.
  • the bottom wall side of the blind hole 49 has a large diameter and the bottom wall side of the freeston 50 has a small diameter, and the pressure oil in the second chamber 53 is within a stroke L range. In this way, the air flows from the passage 57 to the first room 52.
  • the second chamber 53 communicates with the interior of the sleeve 42 through pores 58 formed on the side wall of the port 43, and the interior of the sleeve 42 communicates with the port 48. They are in communication. This constitutes the leak check valve portion 25.
  • FIG. 7 shows a pair of check valves D, which is different from the first embodiment shown in FIG. 4 in that a passage is not provided in the free piston 28. In this case, the valve seat 32 and the valve body 33 need not be provided.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Check Valves (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

Cette invention concerne un clapet anti-retour, lequel comprend une partie clapet anti-retour principale (23) qui permet à un débit d'huile sous pression de s'écouler dans un premier sens depuis un premier orifice (20) vers un second (21), et qui empêche le débit d'huile sous pression de s'écouler dans l'autre sens, à savoir depuis le second orifice vers le premier. Ce clapet anti-retour comprend également une partie fuite (25), laquelle permet de réduire la pression en une partie qui est plus proche du second orifice que de la partie principale lorsque l'alimentation du fluide sous pression est interrompue au moment où l'huile sous pression s'écoule dans le premier sens, ceci de manière à réduire la pression au premier orifice.
PCT/JP1997/000723 1996-03-07 1997-03-07 Clapet anti-retour WO1997033109A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP5017396A JPH09242903A (ja) 1996-03-07 1996-03-07 チェック弁
JP8/50173 1996-03-07

Publications (1)

Publication Number Publication Date
WO1997033109A1 true WO1997033109A1 (fr) 1997-09-12

Family

ID=12851821

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP1997/000723 WO1997033109A1 (fr) 1996-03-07 1997-03-07 Clapet anti-retour

Country Status (2)

Country Link
JP (1) JPH09242903A (fr)
WO (1) WO1997033109A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103090105A (zh) * 2013-01-29 2013-05-08 河海大学常州校区 阀门缓冲器

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6901755B2 (en) * 2002-03-29 2005-06-07 Praxair Technology, Inc. Piston position drift control for free-piston device

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5630723Y2 (fr) * 1975-12-08 1981-07-22

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5630723Y2 (fr) * 1975-12-08 1981-07-22

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
MICROFILM OF JAPANESE UTILITY MODEL, Application No. 126538/1989, (Laid-Open No. 65070/1991) (MITSUBISHI HEAVY INDUSTRIES, LTD.), 25 June 1991. *
MICROFILM OF JAPANESE UTILITY MODEL, Application No. 28276/1987, (Laid-Open No. 135084/1988) (THE FUJIKURA RUBBER LTD.), 5 September 1988. *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103090105A (zh) * 2013-01-29 2013-05-08 河海大学常州校区 阀门缓冲器
CN103090105B (zh) * 2013-01-29 2015-10-28 河海大学常州校区 阀门缓冲器

Also Published As

Publication number Publication date
JPH09242903A (ja) 1997-09-16

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