WO1996020355A1 - Dispositif de frein pour moteur hydraulique - Google Patents
Dispositif de frein pour moteur hydraulique Download PDFInfo
- Publication number
- WO1996020355A1 WO1996020355A1 PCT/JP1995/002701 JP9502701W WO9620355A1 WO 1996020355 A1 WO1996020355 A1 WO 1996020355A1 JP 9502701 W JP9502701 W JP 9502701W WO 9620355 A1 WO9620355 A1 WO 9620355A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston
- friction plate
- hydraulic motor
- pressure
- side friction
- Prior art date
Links
Classifications
-
- 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
- F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
- F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
- F03C1/00—Reciprocating-piston liquid engines
- F03C1/02—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders
- F03C1/06—Reciprocating-piston liquid engines with multiple-cylinders, characterised by the number or arrangement of cylinders with cylinder axes generally coaxial with, or parallel or inclined to, main shaft axis
- F03C1/0678—Control
-
- 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
- F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
- F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
- F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
- F16D55/36—Brakes with a plurality of rotating discs all lying side by side
- F16D55/40—Brakes with a plurality of rotating discs all lying side by side actuated by a fluid-pressure device arranged in or one the brake
-
- 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
- F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
- F16D2055/0004—Parts or details of disc brakes
- F16D2055/0058—Fully lined, i.e. braking surface extending over the entire disc circumference
-
- 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
- F16D2121/00—Type of actuator operation force
- F16D2121/18—Electric or magnetic
Definitions
- the present invention relates to a hydraulic motor brake device used as a hydraulic motor for turning a hydraulic shovel or the like.
- a shaft is rotatably supported in a casing, and a cylinder block is coupled to the shaft so that the shaft can rotate together with the shaft.
- a plurality of cylinder holes are formed in the cylinder block at intervals in the circumferential direction in parallel with the shaft, and a piston is slidably inserted into each cylinder hole.
- a cylinder chamber is formed in the cylinder hole.
- a thrust ball is coupled to the shaft, and a thrust is fitted to the thrust pole along a swash plate.
- the thrust ball and the shoe are configured to be rotatable together with the shaft, and are biased toward the swash plate by a spring.
- the tip of each piston is universally connected to the show.
- a cylinder is used as the hydraulic motor brake device described above.
- a plurality of movable-side friction plates and fixed-side friction plates are alternately mounted on the block and the housing so as to be stacked in a direction parallel to the axis, and pressed against the friction plate by a spring in opposition to the friction plate.
- a piston which is pushed to the opposite side of the friction plate by the pressure oil in the piston pressure receiving chamber is provided, and the piston is pushed by a spring to press-fit the fixed-side friction plate and the movable-side friction plate.
- the cylinder block is put in a braking state to make it impossible to rotate, and high-pressure oil is supplied to the piston pressure receiving chamber of the piston, so that the piston moves against the spring, thereby causing friction on the fixed side.
- the plate and the movable friction plate are separated from each other, and the cylinder block can be rotated with no braking applied.
- a hydraulic motor brake device when high-pressure oil is supplied to the piston pressure receiving chamber, a non-braking state is established, and when high-pressure oil in the piston pressure receiving chamber is discharged, a braking state is established.
- the time is determined by the movement distance and movement speed of the piston, that is, the time required to complete the discharge of the pressure oil in the piston pressure receiving chamber. .
- the time required to complete the discharge of the pressure oil in the piston pressure receiving chamber is determined by the difference between the capacity of the piston pressure receiving chamber during non-braking and the capacity of the piston pressure receiving chamber during braking, that is, the piston. It is determined by the effective volume of the pressure receiving chamber and the outflow speed of the high-pressure oil in the piston pressure receiving chamber.
- a slow return valve consisting of a chinic valve and a throttle is provided in the pressure oil supply circuit of the piston pressure receiving chamber, and high-pressure oil flows smoothly into the piston pressure receiving chamber, so Although braking is not performed, the high-pressure oil in the piston pressure receiving chamber slowly flows out of the throttle, so the brake system is slowly braked.
- the gap between the fixed-side friction plate and the movable-side friction plate is defined by the piston when the brake is not applied, and the position of the piston when the brake is not applied and the position when the brake is applied.
- the effective volume of the piston is small, so that the aperture is remarkably small and the piston is moved slowly to make the brake The time until the switch enters the braking state is extended.
- the reason is that if the piston movement distance is increased, the gap between the fixed-side friction plate and the movable friction plate becomes large, and the fixed-side friction plate and the movable-side friction plate are rattled due to rotational vibration, etc. Since the side friction plate is attached to the cylinder block at an angle, the friction plate may be damaged during braking, or the braking force may be insufficient, so shorten the piston travel distance. This reduces the gap between the fixed-side friction plate and the movable-side friction plate.
- the piston diameter is large, the effective volume is large even if the moving distance is short, but if the piston diameter is large, the housing becomes large and the hydraulic motor becomes large. .
- an electromagnetic switching valve that communicates and shuts off the piston pressure receiving chamber of the brake device and the hydraulic power supply / tank, A controller that energizes the switching valve is provided, and after a predetermined time elapses after a signal to stop the hydraulic motor is input to the controller, the electromagnetic switching valve is energized to connect the piston pressure receiving chamber to the tank.
- the braking device is brought into a braking state.
- the present invention enables the brake state to be gradually changed from the non-braking state, the variation in the time until the braking is reduced, and the hydraulic motor does not increase in size and the manufacturing cost is reduced. It is an object of the present invention to provide a hydraulic motor brake device which can be used. Disclosure of the invention
- a fixed-side friction plate and a movable-side friction plate attached to a housing and a cylinder block of a hydraulic motor, respectively;
- a hydraulic pressure motor brake device having a piston pressure receiving chamber for pressing the frictional plate in a direction away from the friction plates.
- a stopper that regulates a gap between the fixed-side friction plate and the movable-side friction plate when the piston moves in the separating direction; and a stroke in the separating direction of the piston.
- a load pressure detection circuit for detecting a load pressure from a directional control valve that supplies pressure oil to a hydraulic motor is connected to the piston pressure receiving chamber, and the piston is driven by the negative pressure. It is desirable to do it.
- a hydraulic pilot valve that outputs a pilot pressure that switches a directional control valve that supplies hydraulic oil to a hydraulic motor is provided, and the output side of the hydraulic pilot valve is connected to the piston pressure receiving chamber. And the pilot pressure It is also possible to drive the screw.
- a negative pressure or a pilot pressure is used to bring about the braking / non-braking state, so that a switching valve or the like is not required, and the manufacturing cost is reduced.
- FIG. 1 is a longitudinal sectional view of a hydraulic motor including a first embodiment of a brake device according to the present invention.
- FIG. 2 is a sectional view taken along the line ⁇ — ⁇ in FIG.
- FIG. 3 is a sectional view taken along the line m-in in FIG.
- FIG. 4 is a hydraulic circuit diagram of the first embodiment.
- FIG. 5 is a hydraulic circuit diagram of a second embodiment of the brake device according to the present invention. BEST MODE FOR CARRYING OUT THE INVENTION
- a shaft 5 is rotatably supported in a motor housing 3 formed by joining a cylindrical case 1 and an end plate 2, and a cylinder block 4 is spliced to the shaft 5. Rotated with axis 5 You can do it.
- a plurality of cylinder holes 6 are formed in the cylinder block 4 at intervals in the circumferential direction in parallel with the shaft 5, and a piston 7 can slide in each cylinder hole 6. It is inserted in.
- a thrust ball 32 is spliced to the shaft 5. Further, the thrust ball 32 is attached to the swash plate 10 so as to be inclined with respect to the shaft 5. 9 is fitted so that the thrust ball 32 and the shower 9 can rotate together with the shaft 5, and between the thrust ball 32 and the cylinder block 4.
- each piston 7 is universally connected to the show 9 via a ball 31. Then, pressurized oil from a hydraulic source (not shown) is supplied into the pressure receiving chamber 8 of each cylinder hole 6.
- a hydraulic source not shown
- the swash plate 10 is moved together with the shower 9.
- the shaft 5 is rotated together with the cylinder block 4.
- the inner peripheral surface of the case 1 has a stepped shape having a small-diameter inner peripheral surface 11, an intermediate-diameter inner peripheral surface 12, and a large-diameter inner peripheral surface 13.
- the fixed-side friction plate 14 and the movable-side friction plate 15 are mounted on the outer peripheral surface 4 a of the cylinder block 4 so as not to rotate alternately in a direction parallel to the axis 5.
- a plurality of recesses 11 a are formed in the small-diameter inner peripheral surface 11 at intervals in the circumferential direction, and a convex portion 14 a is formed on the outer peripheral surface of the fixed-side friction plate 14.
- a plurality of protrusions are formed at intervals in the direction, and the protrusions 14a are fitted into the recesses 11a.
- the cylinder block A plurality of concave portions 4b are formed on the outer peripheral surface 4a of the work 4 at intervals in the circumferential direction, and a plurality of convex portions 15a are formed on the inner peripheral surface of the movable friction plate 15 at an interval in the circumferential direction.
- the projection 15a is fitted into the recess 4b.
- a ring-shaped stopper 16 such as a snap ring is mounted on the intermediate diameter and peripheral surface 12 of the case 1.
- the stopper 16 is fixed to the fixed-side friction plate 14.
- the clearance between the movable side friction plate 15 and the movable side is specified to be small.
- a piston 17 is slidably fitted into the large-diameter inner peripheral surface 13, the intermediate peripheral surface 12, and the small-diameter inner peripheral surface 11, and the piston 17 is slidably inserted into the large-diameter inner peripheral surface.
- Surface 13, middle inner peripheral surface 12, and small-diameter peripheral surface 11 have a hollow stepped shape with large-diameter base 18, intermediate-diameter middle 19, and small-diameter tip 20.
- a piston pressure receiving chamber 21 is formed.
- the small diameter tip portion 20 is smaller in diameter than the inner diameter of the stopper 16.
- a spring 22 is provided between the end plate 2 and the piston 17, and the spring 17 pushes the piston 17 to the right, so that the small-diameter tip portion 20 is pressed.
- the cylinder block 4 is fixed to the housing 3 by crimping the fixed-side friction plate 14 and the movable-side friction plate 15 by protruding from the tongue 16 toward the friction plate. This is to brake.
- the piston 17 is moved to the left against the spring 22, and the fixed-side friction plate 14 and the movable-side friction plate 1 are moved.
- the cylinder block 4 is brought into the non-braking state by separating the cylinder block 5 from the cylinder block 5.
- a port 23 is formed in the case 1, and the port 23 communicates with the piston pressure receiving chamber 21 through an oil hole 24 as shown in FIG. ing.
- a slow return valve 25 is provided in the oil hole 24, and the slow return valve 25 resonates a port 27 having a fine hole 26 with an oil passage 28 through a spring 28. 4 and a plurality of auxiliary poppets 30 each having a peg hole 29 are sequentially inserted in the inside of the port 27. .
- the brake device is configured in this manner, when high-pressure oil is supplied to the piston pressure receiving chamber 21, the piston 17 moves against the spring 22 until it comes into contact with the end plate 2.
- the tip end surface 17a of 17 moves from the stopper 16 in the direction away from the fixed-side friction plate 14. In that case, the movement distance of the piston 17 is as long as L1.
- the effective volume in the piston pressure receiving chamber 21 becomes large. Therefore, when the piston 17 is pushed by the spring 22 to be in the braking state, Since the amount of oil flowing out of the ton pressure receiving chamber 21 becomes large, even if the opening area of the throttle (pore) of the slow return valve 25 is made large, the piston 17 is fixed to the fixed friction plate. The brake device slowly enters the braking state because the time until 14 and the movable friction plate 15 are crimped is long.
- FIG. 4 shows the hydraulic circuit of the first embodiment.
- reference numeral 40 denotes a hydraulic pump, and a plurality of directional control valves 42 are provided in parallel in a discharge path 41 of the hydraulic pump. Pressurized oil is supplied to the working machine cylinder that does not use it.
- a pressure compensating valve 43 is provided on the inlet side of each directional control valve 42, and the pressure compensating valve 43 is a conventionally known one having a check valve portion 44 and a pressure reducing valve portion 45. Then, the pressure is compensated by the corresponding load pressure P 0 of the actuator and the load pressure P i of the load pressure detection circuit 46. The highest load pressure is introduced to the load pressure detection circuit 46 when a plurality of factories are operated simultaneously.
- the load pressure detection circuit 46 is connected to a piston pressure receiving chamber 21 of a brake device of the hydraulic motor M via a hydraulic timer 47. Since the hydraulic pressure timer 47 is constituted by the check valve 48 and the throttle 49, the load pressure of the load pressure detection circuit 46 flows smoothly into the piston pressure receiving chamber 21. However, the pressurized oil in the piston pressure receiving chamber 21 flows out slowly.
- the load pressure detection circuit 46 is connected to the tank 51 via a throttle 50.
- the hydraulic circuit of the first embodiment is configured as described above, when any one of the directional control valves 42 is not operated (in the neutral position A), the load pressure is applied to the load pressure detection circuit 46. No pressure is generated, and as a result, the pressure in the piston pressure receiving chamber 21 of the brake device becomes almost zero, so that the brake device is in a braking state and the turning hydraulic motor M is braked.
- the brake device is brought into the non-braking state by using the load pressure when the directional control valve 42 is operated, when the hydraulic motor M for turning is rotated or when a working machine cylinder (not shown) is used.
- the brake device is automatically put into the non-braking state when the brake is operated, and the brake is automatically put into the brake state when the hydraulic motor is not rotated or the work equipment cylinder is not operated.
- No switching valve or controller is required to bring the brake device into the braking state / non-braking state.
- the reason why the brake device is put into the non-braking state when the work equipment cylinder is operated is to hold the upper body by hydraulic pressure during the excavation of the hydraulic shovel.
- the hydraulic excavator is provided with an upper body rotatably provided on a lower vehicle body by a hydraulic motor for rotation, and an excavator comprising a boom, an arm and a bucket is mounted on the upper vehicle body by a working machine cylinder. Since it is mounted so that it can rotate, excessive rotational torque acts on the upper body during offset excavation, and if the brake device is in a braking state at that time, a large force is applied to the hydraulic motor (including the reduction gear). This causes problems such as breakage of the hydraulic motor and speed reducer and abnormal noise in the brakes, and it is necessary to hold the upper body hydraulically with the brake device in a non-braking state.
- FIG. 5 shows a Shanto pressure circuit of a second embodiment of the brake device according to the present invention.
- reference numeral 52 denotes a pilot pressure pump, and its discharge path 53 has a hydraulic pilot valve 54 for turning and a working machine.
- a hydraulic pilot valve 55 is provided.
- the first and second output circuits 56 and 57 of the hydraulic pilot valve 54 are connected to the first and second pressure receiving portions 42a and 42b of one of the directional control valves 42, respectively.
- the third and fourth output circuits 58 and 59 of the hydraulic pilot valve 55 are respectively connected to the first and second pressure receiving parts 42 a and 42 b of the other directional control valve 42. ing.
- the high pressure oil (pilot pressure oil) of the first and second output circuits 56, 57 is detected by the first detection circuit 61 by the first shuttle valve 60, and The high pressure oil of the first detection circuit 61 and the third output circuit 58 is detected by the second detection circuit 63 by the second shuttle valve 62, and the second detection circuit 63 63 is connected to the piston pressure receiving chamber 21 of the brake device via the hydraulic timer 47.
- the turning hydraulic pilot 54 is operated in both the forward and reverse directions so as to be connected to the first and second output circuits 56 and 57.
- the pilot pressure oil is supplied to the third output circuit 58.
- the pilot pressure oil is output to the second detection circuit 63, whereby the pressure oil can be supplied into the piston pressure receiving chamber 21 and the brake device is put into a non-braking state c Therefore, the same function and effect as those of the first embodiment can be obtained.
- the hydraulic pump 40 is of a variable displacement type, and its capacity is controlled to increase or decrease by swinging the swash plate 70 with a control screw 71.
- the control piston 71 slides in the capacity increasing / decreasing direction by the self-discharge pressure supplied to the small-diameter pressure receiving chamber 72 and the large-diameter pressure receiving chamber 73, and the large-diameter pressure receiving chamber 73 is controlled by the control valve 74.
- Self-discharge pressure oil is supplied.
- the control valve 74 is switched by the load pressure and the self discharge pressure.
- the effective volume of the piston 17 in the piston pressure receiving chamber 21 increases, and the piston 17 receives the piston 17 in the non-braking state. Since a large amount of pressurized oil flows in, it takes time for the pressurized oil in the piston pressure receiving chamber 21 to flow out, and the braking time becomes longer by that much.
- the braking state is gradually changed from the non-braking state to the braking state.
- the variation in the time until the pressure becomes small can be reduced, and the hydraulic motor does not become large.
- the brake device according to the present invention uses negative pressure or pilot pressure to bring about the braking / non-braking state, no switching valve or the like is required, and the manufacturing cost is reduced.
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Hydraulic Motors (AREA)
- Braking Arrangements (AREA)
Description
Claims
Priority Applications (4)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
US08/849,574 US6006872A (en) | 1994-12-27 | 1995-12-26 | Braking apparatus for a hydraulic motor |
KR1019970704550A KR100326890B1 (ko) | 1994-12-27 | 1995-12-26 | 유압모터의브레이크장치 |
EP95941902A EP0797020B1 (en) | 1994-12-27 | 1995-12-26 | Brake device for a hydraulic motor |
DE69528600T DE69528600T2 (de) | 1994-12-27 | 1995-12-26 | Bremsvorrichtung für einen hydraulischen motor |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP6/325086 | 1994-12-27 | ||
JP6325086A JPH08177899A (ja) | 1994-12-27 | 1994-12-27 | 油圧モータのブレーキ装置 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO1996020355A1 true WO1996020355A1 (fr) | 1996-07-04 |
Family
ID=18172990
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP1995/002701 WO1996020355A1 (fr) | 1994-12-27 | 1995-12-26 | Dispositif de frein pour moteur hydraulique |
Country Status (7)
Country | Link |
---|---|
US (1) | US6006872A (ja) |
EP (1) | EP0797020B1 (ja) |
JP (1) | JPH08177899A (ja) |
KR (1) | KR100326890B1 (ja) |
CN (1) | CN1175299A (ja) |
DE (1) | DE69528600T2 (ja) |
WO (1) | WO1996020355A1 (ja) |
Families Citing this family (12)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP3718080B2 (ja) * | 1999-05-07 | 2005-11-16 | 日立建機株式会社 | ブレーキ装置を有する液圧モータ |
JP4526066B2 (ja) * | 2004-06-28 | 2010-08-18 | 株式会社不二越 | 油圧モータ |
JP4613588B2 (ja) * | 2004-11-11 | 2011-01-19 | トヨタ自動車株式会社 | 自動変速機の摩擦係合装置 |
DE102006025969A1 (de) * | 2006-06-02 | 2007-12-06 | Robert Bosch Gmbh | Hydrostatische Kolbenmaschine und Druckring für eine Bremseinrichtung derselben |
JP5229963B2 (ja) * | 2009-06-30 | 2013-07-03 | 東芝機械株式会社 | スリップ抑制および起動効率を備えた油圧モータ |
JP5523980B2 (ja) * | 2010-08-10 | 2014-06-18 | 東芝機械株式会社 | スリップ抑制および起動効率向上機能を備えた油圧モータ |
DE102011053645A1 (de) * | 2011-09-15 | 2013-03-21 | Linde Material Handling Gmbh | Axialkolbenmaschine mit einem druckmittelgefüllten Gehäuse |
US9908515B2 (en) * | 2015-06-29 | 2018-03-06 | Deere & Company | Drive assembly with multi-function actuator for motor and brake control |
JP7049222B2 (ja) * | 2018-09-10 | 2022-04-06 | Kyb株式会社 | ブレーキシステム及びこれを備える液圧モータ |
JP7281918B2 (ja) * | 2019-02-18 | 2023-05-26 | ナブテスコ株式会社 | 油圧モータ |
CN113107922B (zh) * | 2021-03-16 | 2022-11-04 | 北京天玛智控科技股份有限公司 | 液压马达和调压装置 |
CN117605779B (zh) * | 2024-01-24 | 2024-04-16 | 宁波中意液压马达有限公司 | 一种高压高速液压马达的变量制动结构 |
Citations (5)
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JPS616404A (ja) * | 1984-06-20 | 1986-01-13 | Kayaba Ind Co Ltd | 油圧モ−タの制動装置 |
JPS6193641U (ja) * | 1984-11-26 | 1986-06-17 | ||
JPS62100306U (ja) * | 1985-12-16 | 1987-06-26 | ||
JPH02248724A (ja) * | 1989-03-22 | 1990-10-04 | Honda Motor Co Ltd | 摩擦クラッチのストッパー構造 |
JPH02126933U (ja) * | 1989-03-29 | 1990-10-19 |
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US3680666A (en) * | 1970-01-08 | 1972-08-01 | Sommer Co | Motor brake unit |
US3759357A (en) * | 1972-03-23 | 1973-09-18 | Caterpillar Tractor Co | Brake saver circuit |
US4263991A (en) * | 1977-05-27 | 1981-04-28 | Lambert Brake Company | Combined failsafe and service brake |
DE2739994C2 (de) * | 1977-09-06 | 1979-05-10 | Losenhausen Maschinenbau Ag, 4000 Duesseldorf | Bremssystem für Baumaschinen mit hydraulischem Fahrantrieb |
US4415067A (en) * | 1981-05-29 | 1983-11-15 | Force Control Industries, Inc. | Liquid cooled brake unit |
JPS5876463U (ja) * | 1981-11-19 | 1983-05-24 | 株式会社小松製作所 | 油圧モ−タのブレ−キ解放装置 |
DE3245720C2 (de) * | 1982-12-10 | 1984-12-20 | Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart | Antriebsanordnung für einen Dreh-, Schwenk- und Fahrantrieb eines Fahrzeugs, insbesondere für einen Bagger |
FR2541382B1 (fr) * | 1983-02-21 | 1987-07-03 | Poclain Sa | Procede et circuit de commande d'un moteur associe a un frein de securite |
JPS6087882A (ja) * | 1983-10-18 | 1985-05-17 | ジェイエスアール株式会社 | 振動選別機 |
US4607730A (en) * | 1983-12-09 | 1986-08-26 | Deere & Company | Brake mechanism |
DE4008362A1 (de) * | 1990-02-13 | 1991-08-14 | Kinshofer Greiftechnik | Hydromotor |
DE4104712C2 (de) * | 1991-02-15 | 1995-11-16 | Rexroth Mannesmann Gmbh | Radialkolbenmaschine mit mechanischer Bremseinrichtung |
US5186284A (en) * | 1991-05-31 | 1993-02-16 | Case Corporation | Fail safe self-adjusting disc brake |
DE4214397C2 (de) * | 1992-04-30 | 1995-07-06 | Hydromatik Gmbh | Hydrostatischer Motor mit einer Bremseinrichtung |
US5601160A (en) * | 1994-10-20 | 1997-02-11 | Case Corporation | Hydraulically actuated brake assembly for an off-highway implement |
-
1994
- 1994-12-27 JP JP6325086A patent/JPH08177899A/ja active Pending
-
1995
- 1995-12-26 DE DE69528600T patent/DE69528600T2/de not_active Expired - Fee Related
- 1995-12-26 WO PCT/JP1995/002701 patent/WO1996020355A1/ja active IP Right Grant
- 1995-12-26 US US08/849,574 patent/US6006872A/en not_active Expired - Fee Related
- 1995-12-26 KR KR1019970704550A patent/KR100326890B1/ko not_active IP Right Cessation
- 1995-12-26 EP EP95941902A patent/EP0797020B1/en not_active Expired - Lifetime
- 1995-12-26 CN CN95197547A patent/CN1175299A/zh active Pending
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS616404A (ja) * | 1984-06-20 | 1986-01-13 | Kayaba Ind Co Ltd | 油圧モ−タの制動装置 |
JPS6193641U (ja) * | 1984-11-26 | 1986-06-17 | ||
JPS62100306U (ja) * | 1985-12-16 | 1987-06-26 | ||
JPH02248724A (ja) * | 1989-03-22 | 1990-10-04 | Honda Motor Co Ltd | 摩擦クラッチのストッパー構造 |
JPH02126933U (ja) * | 1989-03-29 | 1990-10-19 |
Also Published As
Publication number | Publication date |
---|---|
KR980701069A (ko) | 1998-04-30 |
CN1175299A (zh) | 1998-03-04 |
EP0797020A4 (en) | 1998-10-07 |
DE69528600D1 (de) | 2002-11-21 |
US6006872A (en) | 1999-12-28 |
EP0797020B1 (en) | 2002-10-16 |
EP0797020A1 (en) | 1997-09-24 |
DE69528600T2 (de) | 2003-06-18 |
JPH08177899A (ja) | 1996-07-12 |
KR100326890B1 (ko) | 2002-08-13 |
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