WO1996023979A1 - Systeme de freinage pour corps a deplacement lineaire - Google Patents
Systeme de freinage pour corps a deplacement lineaire Download PDFInfo
- Publication number
- WO1996023979A1 WO1996023979A1 PCT/JP1996/000121 JP9600121W WO9623979A1 WO 1996023979 A1 WO1996023979 A1 WO 1996023979A1 JP 9600121 W JP9600121 W JP 9600121W WO 9623979 A1 WO9623979 A1 WO 9623979A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- brake
- rod
- brake member
- force
- piston
- Prior art date
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/26—Locking mechanisms
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D63/00—Brakes not otherwise provided for; Brakes combining more than one of the types of groups F16D49/00 - F16D61/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
- F15B15/20—Other details, e.g. assembly with regulating devices
- F15B15/26—Locking mechanisms
- F15B15/262—Locking mechanisms using friction, e.g. brake pads
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D59/00—Self-acting brakes, e.g. coming into operation at a predetermined speed
- F16D59/02—Self-acting brakes, e.g. coming into operation at a predetermined speed spring-loaded and adapted to be released by mechanical, fluid, or electromagnetic means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
- F16D63/00—Brakes not otherwise provided for; Brakes combining more than one of the types of groups F16D49/00 - F16D61/00
- F16D63/008—Brakes acting on a linearly moving member
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
- Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y10S16/00—Miscellaneous hardware, e.g. bushing, carpet fastener, caster, door closer, panel hanger, attachable or adjunct handle, hinge, window sash balance
- Y10S16/17—Checks and closers, holding means
Definitions
- the present invention relates to a brake device for applying a brake to a piston rod of an air cylinder or a guide opening of a linear moving body by frictional force and stopping the braking device.
- a force in a linear motion direction is used as a braking force.
- the present invention relates to a linear moving body brake device that can be used for preventing a linear moving body from falling and for making an emergency stop by enabling the device to be reduced in size and cost.
- US Pat. 4, 791, 8555 describes a device that applies a brake to stop a piston rod of an air cylinder by frictional force. I have.
- This prior invention employs a mechanism for rotating the brake member by rotating the brake member in a direction perpendicular to the linear motion, so that the force in the linear motion direction cannot be used for the braking force. For this reason, a strong spring force and a complicated car mechanism are required, and the manufacturing cost is high and the apparatus is large.
- US Pat. 4, 981, 069 also describe a device for stopping the piston port of the air cylinder by applying a brake by frictional force.
- This prior invention employs a mechanism in which the brake member is elastically deformed in a direction perpendicular to the linear motion and the reaction force is used as the braking force, and this also cannot use the force in the linear motion direction as the braking force. . For this reason, a strong elastic deformation force is required, and further, a strong brake release force is required. In addition, since the elastic deformation force is used, there is a problem in that the braking force varies and the braking force is reduced, so that extremely high processing accuracy is required. This is a factor that increases the size of the force device or increases the manufacturing cost.
- a ring-shaped brake member is fitted into a piston rod of an air cylinder with a loose fit, and the brake member is tilted in the axial direction of the rod by a spring force to reduce frictional force.
- An air cylinder has been manufactured to generate the air cylinder and further increase its tilt by the thrust of the air cylinder to lock the biston rod.
- This brake device is similar to the present invention in that the force in the linear motion direction is used for the braking force, but has an important difference in the shape of the fitting surface between the piston rod and the through hole of the brake member. There is.
- this brake device when a rotational moment is given to the brake member by the spring and the thrust of the air cylinder, and the brake member is tilted to apply the brake, most of the reaction force of the rotational moment becomes the rotational moment.
- the most part of the braking force applied to the piston port is a value obtained by multiplying the reaction force parallel to the rotational moment by the coefficient of friction.
- the ordinary friction coefficient is about 0.2, and there is a problem that a large reaction force is required to generate an effective braking force in this brake device.
- a method of increasing a spring force and increasing a distance between fulcrum points of a rotating moment generated by a thrust of an air cylinder, and a dimension of a brake member in a linear motion direction in order to generate a large reaction force, a method of increasing a spring force and increasing a distance between fulcrum points of a rotating moment generated by a thrust of an air cylinder, and a dimension of a brake member in a linear motion direction.
- the former causes an increase in the size of the brake device and is not suitable for practical use, and the latter has a problem that the contact surface pressure of the piston rod is increased, the outer periphery of the piston rod is easily damaged, and the brake member is easily damaged. Disclosure of the invention
- An object of the present invention is to provide a brake device for applying a brake to a linear moving body and stopping it, which can be manufactured at a small size and at a low cost, and which can be used for drop prevention or emergency stop only. It is an object of the present invention to provide a suitable linear moving body brake device.
- a brake device according to the present invention is provided with a hole in a brake member, and a rod in the hole.
- the brake member is the axis of the rod.
- a notch with a width smaller than the hole is formed at a symmetrical position in the hole along a plane that includes the fulcrum and the axis of the rod. It is characterized by.
- a rotational force (rotational moment) is applied to the brake member to generate an anti-force on the mating surface in the hole.
- the frictional force due to power is defined as the reaction force of the rotational force.
- the reaction force from the rod generated when a torque (rotational moment) M is applied to the brake member is converted into a component force (sum of absolute values) R parallel to the torque M.
- the component force (sum of the absolute values) r perpendicular to the rotational force M and if we consider that the rotational radius of each of the component forces is L and the friction coefficient is k, the following equation holds .
- FIG. 1 shows an embodiment of the present invention, in which a brake is released from an air cylinder brake device. It is an axial sectional view of a state.
- FIG. 2 is a cross-sectional view of the same device.
- FIG. 3 is an axial sectional view of the device in a brake state.
- FIG. 4 is an axial sectional view of a brake device according to another embodiment.
- FIG. 5 is a cross-sectional view of the same device.
- FIG. 6 is an axial sectional view of the device in a brake state.
- FIG. 7 is a front view of a brake member according to another embodiment.
- FIG. 8 is a sectional view of FIG.
- FIG. 9 is a partial sectional view of a brake member and a rod according to another embodiment.
- FIG. 10 is an axial cross-sectional view of a fall prevention device for a steel rod to which the present invention is applied.
- FIG. 11 is a cross-sectional view of FIG. BEST MODE FOR CARRYING OUT THE INVENTION
- FIG. 1 to 3 show a brake device for an air cylinder.
- a casing 1 is fixedly mounted on a tip end of an air cylinder 20, and a piston rod 21 penetrates through the casing 1.
- a plate-shaped brake member 2 and a brake member 3 as shown in the figure are disposed with a gap therebetween, and the brake member 2 is provided so as to be tiltable with its lower end as a fulcrum. 3 is disposed so that the upper part thereof can be tilted about a fulcrum.
- the brake member 2 is used for braking when the piston rod is pushed out, and the brake member 3 is used for braking when pulled back.
- insertion holes 4 and 5 for passing the piston rod 21 are formed, and the insertion holes 4 and 5 allow the piston rod 21 to be fitted with a clearance fit.
- Notches 4a and 5a (concave portions) are provided so as to extend at the upper and lower portions in the circular hole.
- the widths of the notches 4a and 5a are smaller than the diameter of the circular holes of the through holes 4 and 5, and are about 90% of the diameter.
- the diameter of the circular holes of the through holes 4 and 5 is formed slightly larger than the outer diameter of the piston rod 21 to form a loose fit, and the width of the rectangular cutouts 4 a and 5 a is It is formed smaller than the diameter of piston rod 21.
- the outer diameter of the biston rod 21 is 20 strokes
- the diameter of the circular holes of the through holes 4 and 5 is 20.;! ⁇ 20.2 mm, and the rectangular cutouts 4 a and 5 a
- the width is formed in 18 rows.
- the piston rod 21 is inserted into the through holes 4 and 5 of the two brake members 2 and 3, and the brake members 2 and 3 are loosely externally attached to the outer periphery of the piston rod 21 in the casing 1. Will be fitted.
- Coil springs 6 and 7 are interposed between the upper and lower portions between the two brake members 2 and 3, and bias the brake members 2 and 3 in a direction separating them by the spring force.
- the coil springs 6 and 7 are mounted so that both ends are inserted into holes provided on one surface of both brake members 2 and 3.
- One brake member 2 is formed to be slightly longer than the other brake member 3, and the lower end of the brake member 2 is loosely inserted into a rectangular opening 8 formed at the bottom of the casing 1.
- the upper ends of both brake members 2 and 3 project upward from rectangular opening 9 formed in the upper part of casing 1.
- the front side of the opening 9 is formed large so as to have a margin (space), and the brake member 2 can incline to the front, that is, the pushing side in a certain range.
- the upper coil spring 6 acts to press the brake member 3 against the rear end of the opening 9, that is, the contact end surface 11 on the retraction side
- the lower coil spring 7 acts as a brake.
- the rake member 2 acts to press the rake member 2 against the contact end surface 12 on the front side of the opening 8, that is, on the pushing side.
- a contact end face 13 is formed on the rear side of the opening 8, that is, on the retraction side.
- the positions of the end surface 13 of the opening 8 and the end surface 11 of the upper opening 9 are determined by the brake release piston 15 described later so that the brake members 2 and 3 are pulled back.
- the brake release piston 15 When pressed, the lower part of the brake member 2 contacts the end face 13, and the upper part of the brake member 3 contacts the end face 11, and at this time, the brake members 2, 3 move in the axial direction of the piston rod 21. So that the brakes are released Formed.
- a cylinder chamber 10 is formed at a front portion in the casing 1, and a brake release piston 15 is slidably fitted into the cylinder chamber 10. Since the piston rod 21 is passed through the center of the cylinder chamber 10, the piston 15 is disposed so as to be slidably fitted to the outer periphery of the piston rod 21. In addition, a bulge is provided at the center of the tip of the piston 15, and the bulge pushes the brake member 2 back.
- An air supply port 16 for supplying air into the cylinder chamber 10 is provided above the casing 1.
- Seal members are attached to the outer and inner peripheral portions of the piston 15 for releasing the brake, and the seal member is also attached to the support portion of the piston rod 21 at the front of the casing 1. .
- the piston 15 When exhausting from the boat 16 provided in the casing 1, the piston 15 becomes free, and the brake members 2 and 3 are actuated by the spring forces of the coil springs 6 and 7, as shown in Fig. 3. To tilt. At this time, the brake members 2 and 3 are given initial rotational force (rotational moment) with the end surfaces 12 and 11 as fulcrums by the coil springs 6 and 7, respectively, and the reaction force of the rotational force is applied to the brake members 2 and 3. A frictional force is generated between the brake members 2, 3 and the rod 21 in accordance with the reaction force generated on the mating surface of the piston port 21 in the through holes of the first and third pistons. Occurs in the initial state.
- the inner surfaces of the through holes 4 and 5 of the brake members 2 and 3, that is, the shape of the fitting surfaces of the piston rod 21 and the brake members 2 and 3 are the upper portions of the holes that can be loosely fitted with the piston rod 21. And the lower part is cut out.
- the notches 4a and 5a are formed at symmetrical positions in the through holes along the plane including the fulcrum of the brake members 2 and 3 and the axis of the rod, and the width of the notches 4a and 5a is ⁇ Through holes 4, 5 smaller than the mystery. Therefore, when the brake members 2 and 3 are tilted and a rotational force is applied with the end surface 12 or 11 as a fulcrum, the reaction force received by the rod 21 from the fitting surface of the brake member is reduced by the notch 4a. 5a, there is almost no component force parallel to the rotational moment, and a large component force perpendicular to the rotational moment. For this reason, a large frictional force is generated on the mating surface, and a strong braking force can be generated.
- the brake device has a piston rod outer diameter of 2 O mm, an axial thickness of the brake member of 15 mm, a cut-out width of 18 mm for the insertion hole of the brake member, and an outer diameter of the piston 15 of 6 mm.
- the brake device having the above configuration was manufactured by setting the piston rod material to 3 mm, the material of the piston rod to carbon steel (carbon 0.5%), and the material of the brake member to ductile iron.
- the brake when the brake is applied in the direction of gravity, the brake can be applied by the gravity of the brake member itself without using spring. .
- the release of the piston brake can also be performed by an electromagnetic solenoid or manually.
- the brake device that applies a brake to both sides in the linear motion direction is shown. However, a brake device that applies a brake to only one side may use only one brake member and one spring.
- FIGS. 4 to 6 show an embodiment in which the present invention is applied to a brake device for a moving part of a mouthless cylinder.
- This brake device is used for braking a guide table 22 of a moving table of a rodless cylinder (not shown).
- FIGS. 4 to 6 parts having the same structure as in the above embodiment are denoted by the same reference numerals, and description thereof will be omitted.
- a casing 1 is fixed to a moving table of a rodless cylinder and guides a moving table or a linear moving body connected to the moving table. Communicated within.
- the structure of the casing 1, the brake members 2, 3, the cylinder chamber 10, the brake release button 15, and the like disposed therein are exactly the same as those of the above embodiment.
- the shape of the notch of the circular hole of the brake member may be a notch formed of a part of the outer peripheral portion of the cylinder as shown in FIGS. . That is, in the brake member 33 shown in FIGS. 7 and 8, a through hole 35 is formed, for example, at the upper and lower portions of a circular hole having a diameter of 12 by a cutout portion 35 a forming a part of the outer periphery of the cylinder. It is formed by extending.
- the notch 35a can be formed, for example, by inserting a drill having an outer diameter of 11 mm into the circular insertion hole 35 at an angle of, for example, 5 ° with respect to the axis of the circular insertion hole 35.o
- a circular through hole 37 is formed in the brake member 36, and the upper and lower surfaces of the piston rod 38 are dropped horizontally, so that the upper part of the outer peripheral portion of the rod is formed.
- a flat portion 38a (a cutout portion) may be provided at the lower part of the frame.
- the above-mentioned brake device is very simple only by arranging the brake member 23 which has a relatively simple shape and does not require much dimensional accuracy in the casing 1 and providing the actuator for releasing the brake. Since it can be easily configured, it can be manufactured in a small size and at low cost, and can be used for emergency stop or intermediate stop of a piston rod of a hydraulic cylinder. It can also be used effectively as a brake device for stopping and for preventing the piston rod or suspended object from falling when stopped.
- FIG. 10 and FIG. 11 show an embodiment in which the present brake device is applied to a fall prevention of a piston rod of an air cylinder.
- a piston 41 is slidably fitted in a cylinder of a cylinder body 49.
- a piston rod 42 is attached to the front of the piston 41, followed by a brake rod 43.
- the brake opening may be formed integrally with the piston rod 42.
- the brake member 44 inserted into the end of the cylinder body 49 has a cylindrical shape having a cylindrical outer surface smaller than the cylindrical inner surface of the cylinder body 49, and a protrusion 50 is provided at a lower portion thereof.
- the sealing material 53 is fitted around the outer periphery.
- the brake member 44 has its protrusion 50 engaged with the cylinder side, and the brake member 44 can be tilted in a plane including the axis of the pad 43 with the protrusion 50 as a fulcrum. Is inserted. A hole is provided at the center of the brake member 44 to partially fit the brake port 43, and a hole for attaching the spring 45 is provided at the top.
- the brake member 44 is assembled in the cylinder body 49 by a snap ring 47, and is mounted so as to be slightly (about 5 degrees) tiltable with the contact position of the protrusion 50 as a fulcrum.
- a spring 45 attached between the spring receiver 46 and the brake member 44 gives the brake member 44 an initial rotational force (rotational moment).
- the brake member 44 overcomes the force of the spring 45 and is pressed against the snap ring 47, making a right angle with the brake rod 43, and releasing the brake. 1 makes normal movement.
- the brake member 44 is tilted by the spring 45.
- the spring force is extremely small, and the brake rod 43 is a hole in the brake member 44. Is fitted to.
- the brake member 44 is tilted by a spring 45 by applying a rotational force about the projection 50 as a fulcrum. The reaction force of this rotational force causes the brake rod 43 A friction force is generated between the rake member 4 and the rake member 4.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Electromagnetism (AREA)
- Braking Arrangements (AREA)
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US08/702,698 US5823300A (en) | 1995-01-31 | 1996-01-24 | Brake device of linear moving body |
KR1019960705044A KR100259746B1 (ko) | 1995-01-31 | 1996-01-24 | 직선이동체의 브레이크장치 |
EP96901102A EP0753670B1 (en) | 1995-01-31 | 1996-01-24 | Brake system for linearly movable bodies |
DE69610798T DE69610798T2 (de) | 1995-01-31 | 1996-01-24 | Bremssystem für einen bewegbaren körper |
Applications Claiming Priority (6)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP7/50302 | 1995-01-31 | ||
JP5030295A JPH08210315A (ja) | 1995-01-31 | 1995-01-31 | エァーシリンダ用ブレーキ装置 |
JP7/104524 | 1995-03-23 | ||
JP10452495A JPH08261257A (ja) | 1995-03-23 | 1995-03-23 | 直線運動用ブレーキ装置 |
JP7/351722 | 1995-12-15 | ||
JP35172295A JPH09166108A (ja) | 1995-12-15 | 1995-12-15 | 落下防止付きエアシリンダ。 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1996023979A1 true WO1996023979A1 (fr) | 1996-08-08 |
Family
ID=27293920
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP1996/000121 WO1996023979A1 (fr) | 1995-01-31 | 1996-01-24 | Systeme de freinage pour corps a deplacement lineaire |
Country Status (5)
Country | Link |
---|---|
US (1) | US5823300A (ja) |
EP (1) | EP0753670B1 (ja) |
KR (1) | KR100259746B1 (ja) |
DE (1) | DE69610798T2 (ja) |
WO (1) | WO1996023979A1 (ja) |
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JP2010502164A (ja) * | 2006-08-21 | 2010-01-21 | イリノイ トゥール ワークス インコーポレイティド | リニアモーターのブレーキ |
EP4250552A3 (en) * | 2017-09-15 | 2023-11-29 | Illinois Tool Works Inc. | Braking system for electromagnetic motors |
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CH689114A5 (de) * | 1996-08-23 | 1998-10-15 | Pwb Ag | Feststellvorrichtung einer Linearbewegungseinheit. |
IT1295302B1 (it) * | 1997-10-09 | 1999-05-04 | Tecnofluid Eng Srl | Dispositivo a pistoni per il bloccaggio in posizioni di elementi lineari mobili in traslazione |
DE19749477C2 (de) * | 1997-11-08 | 2001-07-05 | Numatics Gmbh | Feststellvorrichtung |
JP3856934B2 (ja) * | 1998-01-27 | 2006-12-13 | Smc株式会社 | ロック機構付き流体圧シリンダ |
WO1999038645A1 (de) * | 1998-01-28 | 1999-08-05 | Frenotech Establishment | Feststelleinrichtung |
US6019367A (en) * | 1998-08-31 | 2000-02-01 | Xerox Corporation | Printer mailbox compiler-finisher carriage safety stop system |
JP3390144B2 (ja) * | 1999-02-25 | 2003-03-24 | エスエムシー株式会社 | ロック機構付き流体圧シリンダ |
DE19924390A1 (de) * | 1999-05-27 | 2000-11-30 | Volkmann Gmbh & Co | Spulenrahmen |
JP3672782B2 (ja) * | 1999-12-08 | 2005-07-20 | Smc株式会社 | クランプ装置 |
DE10161126A1 (de) * | 2000-12-13 | 2002-06-20 | Lear Corp | Fahrzeugsitzantrieb mit einem mechanischen linearen Raupenbewegungsantrieb |
US6976288B1 (en) * | 2003-02-03 | 2005-12-20 | Valentin Luca | Rod gripper |
US6959852B2 (en) * | 2003-09-29 | 2005-11-01 | Ethicon Endo-Surgery, Inc. | Surgical stapling instrument with multistroke firing incorporating an anti-backup mechanism |
DE10359845B4 (de) * | 2003-12-19 | 2007-03-15 | Moll System- und Funktionsmöbel GmbH | Schrägstellvorrichtung für Möbelstücke |
WO2005113407A1 (en) * | 2004-05-21 | 2005-12-01 | EBL SYSTEMS AB Company Reg NO. 556685-9251 | A lifter provided with a safety stop |
DE102004057581B4 (de) * | 2004-11-30 | 2008-07-03 | Bosch Rexroth Teknik Ab | Feststelleinheit, insbesondere für Druckmittelzylinder |
CN104214248B (zh) * | 2014-08-15 | 2017-05-24 | 无锡怡生医疗设备有限公司 | 一种桥塔滑台刹车装置 |
KR101512471B1 (ko) | 2014-09-11 | 2015-04-16 | 한국뉴매틱(주) | 록-블록을 이용한 로드부재 록킹장치 |
CN104308564B (zh) * | 2014-09-26 | 2017-12-08 | 台州市良曜成套设备有限公司 | 直线导轨组件的滑块刹车机构和棒材截料机的抬料装置 |
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DK154523C (da) * | 1984-02-23 | 1989-05-16 | Wassmann Mogens | Laasering og anvendelse af laaseringen |
US4791855A (en) * | 1985-03-11 | 1988-12-20 | Pubot Giken Co., Ltd. | Cylinder locking device |
US4981069A (en) * | 1988-06-23 | 1991-01-01 | Akio Matsui | Cylinder locking device |
JPH0338487A (ja) * | 1989-07-05 | 1991-02-19 | Honda Motor Co Ltd | リム用付着物除去装置 |
US5224681A (en) * | 1990-04-13 | 1993-07-06 | Lundstrom Donald A | Hand releasable locking collar |
US5131115A (en) * | 1991-01-28 | 1992-07-21 | J. Sarto Co. | Variable position door holder and stop |
US5529148A (en) * | 1993-08-24 | 1996-06-25 | O'leary; Thomas M. | Automatic brake and hold mechanism for sliding rods |
-
1996
- 1996-01-24 KR KR1019960705044A patent/KR100259746B1/ko not_active IP Right Cessation
- 1996-01-24 US US08/702,698 patent/US5823300A/en not_active Expired - Fee Related
- 1996-01-24 EP EP96901102A patent/EP0753670B1/en not_active Expired - Lifetime
- 1996-01-24 DE DE69610798T patent/DE69610798T2/de not_active Expired - Fee Related
- 1996-01-24 WO PCT/JP1996/000121 patent/WO1996023979A1/ja active IP Right Grant
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JPS5752404Y2 (ja) * | 1977-11-25 | 1982-11-15 | ||
JPS59223551A (ja) * | 1983-06-01 | 1984-12-15 | Japan Raisensaa:Kk | 空気圧シリンダ用ブレ−キ装置 |
JPH0338487Y2 (ja) * | 1985-09-27 | 1991-08-14 |
Non-Patent Citations (1)
Title |
---|
See also references of EP0753670A4 * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP2010502164A (ja) * | 2006-08-21 | 2010-01-21 | イリノイ トゥール ワークス インコーポレイティド | リニアモーターのブレーキ |
EP4250552A3 (en) * | 2017-09-15 | 2023-11-29 | Illinois Tool Works Inc. | Braking system for electromagnetic motors |
Also Published As
Publication number | Publication date |
---|---|
DE69610798T2 (de) | 2001-03-01 |
US5823300A (en) | 1998-10-20 |
EP0753670B1 (en) | 2000-11-02 |
KR970701835A (ko) | 1997-04-12 |
KR100259746B1 (ko) | 2000-07-01 |
EP0753670A4 (en) | 1997-05-07 |
EP0753670A1 (en) | 1997-01-15 |
DE69610798D1 (de) | 2000-12-07 |
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