EP0855468A1 - Compresseur-concasseur - Google Patents

Compresseur-concasseur Download PDF

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Publication number
EP0855468A1
EP0855468A1 EP96933627A EP96933627A EP0855468A1 EP 0855468 A1 EP0855468 A1 EP 0855468A1 EP 96933627 A EP96933627 A EP 96933627A EP 96933627 A EP96933627 A EP 96933627A EP 0855468 A1 EP0855468 A1 EP 0855468A1
Authority
EP
European Patent Office
Prior art keywords
ramming
valve means
boom
pressure
floating
Prior art date
Legal status (The legal status 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 status listed.)
Withdrawn
Application number
EP96933627A
Other languages
German (de)
English (en)
Other versions
EP0855468A4 (fr
Inventor
Shigeru Oyama Factory of Komatsu Ltd. SHINOHARA
Takayuki Oyama Factory of Komatsu Ltd. MUTOU
Tadao Oyama Factory of Komatsu Ltd. KARAKAMA
Mitsuru Oyama Factory of Komatsu Ltd. ARAI
Koichi Oyama Factory of Komatsu Ltd. MORITA
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Komatsu Ltd
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 EP0855468A1 publication Critical patent/EP0855468A1/fr
Publication of EP0855468A4 publication Critical patent/EP0855468A4/fr
Withdrawn legal-status Critical Current

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Classifications

    • E—FIXED CONSTRUCTIONS
    • E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
    • E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
    • E01C23/00—Auxiliary devices or arrangements for constructing, repairing, reconditioning, or taking-up road or like surfaces
    • E01C23/06—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road
    • E01C23/12—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road for taking-up, tearing-up, or full-depth breaking-up paving, e.g. sett extractor
    • E01C23/122—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road for taking-up, tearing-up, or full-depth breaking-up paving, e.g. sett extractor with power-driven tools, e.g. oscillated hammer apparatus
    • E01C23/124—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road for taking-up, tearing-up, or full-depth breaking-up paving, e.g. sett extractor with power-driven tools, e.g. oscillated hammer apparatus moved rectilinearly, e.g. road-breaker apparatus with reciprocating tools, with drop-hammers
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/30—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets with a dipper-arm pivoted on a cantilever beam, i.e. boom
    • E02F3/32—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets with a dipper-arm pivoted on a cantilever beam, i.e. boom working downwardly and towards the machine, e.g. with backhoes
    • E02F3/325—Backhoes of the miniature type
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/96—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements
    • E02F3/963—Arrangements on backhoes for alternate use of different tools
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/96—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements
    • E02F3/966—Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements of hammer-type tools
    • 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
    • E02F9/20—Drives; Control devices
    • E02F9/2058—Electric or electro-mechanical or mechanical control devices of vehicle sub-units
    • E02F9/2095—Control of electric, electro-mechanical or mechanical equipment not otherwise provided for, e.g. ventilators, electro-driven fans
    • 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
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • E02F9/221—Arrangements for controlling the attitude of actuators, e.g. speed, floating function for generating actuator vibration
    • 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
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2264—Arrangements or adaptations of elements for hydraulic drives
    • E02F9/2267—Valves or distributors
    • 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
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F3/00—Dredgers; Soil-shifting machines
    • E02F3/04—Dredgers; Soil-shifting machines mechanically-driven
    • E02F3/28—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
    • E02F3/30—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets with a dipper-arm pivoted on a cantilever beam, i.e. boom
    • E02F3/32—Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets with a dipper-arm pivoted on a cantilever beam, i.e. boom working downwardly and towards the machine, e.g. with backhoes

Definitions

  • the present invention relates to a combined ramming and breaking work machine for carrying out a ramming operation as well as a breaking operation by the use of a power shovel or the like.
  • a combined ramming and breaking work machine which comprises: a boom means mounted on a vehicle body so as to be capable of being vertically swung and adapted to be driven by a boom cylinder means; an arm means mounted to the said boom means so as to be capable of being swung vertically and adapted to be driven by an arm cylinder means; a fluid pressure driven vibration generating means operatively coupled to the said arm means; a breaker chisel and a ramming tool which are adapted to be interchangeably and each operatively coupled to the said vibration generating means; and a floating state switching means for rendering the said boom cylinder means in a floating state selectively where a ramming operation is carried out.
  • a breaker chisel or a ramming tool can selectively be employed in a single working machine for carrying on a breaking operation or a ramming operation, respectively, as desired at a given work site.
  • the machine is designed, where a ramming operation should be selectively performed, to render the boom cylinder assembly in a floating state, thus permitting such a ramming work to be carried out efficiently on a single dual purpose working machine.
  • the said floating state switching means may desirably comprise: a first operation sensing means for detecting a condition representing the said vibration generating means being in an operating state; a selector switch means for selectively providing a breaking command and a ramming command; a float valve means disposed in a circuit lying between the said boom cylinder means and a boom valve means for delivering a pressure fluid thereto; a floating switch valve means for controlling the said float valve means to change its position from one to another; and a timer relay means operative, only when both a condition representing signal from the said first operation sensing means and the said ramming command from the said selector switch means are inputted, for acting on the said floating switch valve means to establish a floating position in the float valve means.
  • the said first operation sensing means may preferably comprise a pressure switch means responsive to a pressure in a pilot circuit means lying between a service valve means for delivering a pressure fluid to the said vibration generating means and a hydraulic pilot valve means for controlling the said service valve means.
  • the said floating state switching means may desirably comprise: a selector switch means for selectively providing a breaking command and a ramming command; a float valve means disposed in a circuit lying between the said boom cylinder means and a boom valve means for delivering a pressure fluid thereto; a floating switch valve means for controlling the said float valve means to change its positions from one to another; a second operation sensing means for detecting a condition representing the said boom cylinder means being in an operating state and proving an output signal in response to the said condition; and a timer relay means selectively operative, only when the said output signal from the said second operation sensing means is not inputted and the said ramming command from the said selector switch means is inputted, for acting on the said floating switch valve means to establish a floating position in the said float valve means.
  • the said second operation sensing means may preferably comprise: a shuttle valve means responsive to a higher of pressures of pressure fluids acting on a first pressure receiving portion and a second pressure receiving portion of the said boom valve means from a fluid pressure operated pilot valve means that operates said boom valve means in a controlled manner; and a pressure switch means responsive to a pressure of the said shuttle valve means at its output side.
  • a float switch means and the said timer relay means be selectively operable, only when both an ON signal from the said float switch means and the said ramming command from the said selector switch means are inputted and further an output signal from the said pressure switch means is not inputted, for acting on the said floating switch valve means to establish the floating position in the said float valve means.
  • the said floating state switching means may desirably include: a boom valve means adapted to deliver a pressure fluid to the said boom cylinder means and having a floating position; and a fluid pressure operated pilot valve means for operating the said boom valve means in a control manner, the said pilot valve means having a detent mechanism and further adapted, when operated in a full stroke mode, to switch the said boom valve means to take the said floating position.
  • the said vibration generating means preferably has a body portion formed with a bore adapted to accept a working tool, the said bore having a cap adapted to be detachably fitted thereto, the cap having a hook appended thereto.
  • a working vehicle comprises a an upper vehicle body 3 that is turnably mounted on a lower vehicle body 2 having a traveling body 1 equipped therefor.
  • the upper vehicle body 3 has a driver's seat 4 with a plurality of driving members 5.
  • the upper vehicle body 3 also has a boom member 6 mounted thereon as capable of being swung vertically and being driven by a boom cylinder assembly 7.
  • the boom member 6 has an arm member 8 mounted thereto as capable of being vertically swung and being driven by an arm cylinder assembly 9.
  • the arm member 8 has a bucket member 10 mounted thereto as capable of being turnable vertically and being driven by a bucket cylinder assembly 11. And it is these component that constitute a power shovel.
  • the arm member 8 has a vibration generating unit 12 securely received therein.
  • the vibration generating unit 12 has a body portion 13 in which a piston 14 is slidably received having a pair of pressure receiving chambers at its both end sides.
  • the piston 14 is adapted to be reciprocated with a pressure fluid supplied alternately into these chambers.
  • its body portion 13 is designed to accommodate a breaker chisel 15 and a ramming tool 16 interchangeably.
  • a hydraulic pump 18 is adapted to be driven by means of an engine 17 mounted on the upper vehicle body 3. It has its discharge outlet connected to a boom valve 19, an arm valve 20, a bucket valve 21 and the inlet port of a service valve 22.
  • the boom valve 19 has a first and a second actuator port 23 and 24 which are connected via a first and a second fluid circuit 25 and 26 to the boom cylinder assembly 7 at its elongating and retracting chambers 7a and 7b, respectively.
  • the service valve 22 has an actuator port 27 that is connected to the vibration generating unit 12 via a fluid circuit 28.
  • a float valve 29 is provided at a site both midway of the first circuit 25 and midway of the second circuit 29.
  • the float valve 29 is held by spring means to take its position of fluid communication a and is adapted to be switched to a floating position b under a pressure fluid supplied into its pressure receiving chamber 30 to establish a fluid communication of the elongating and retracting chambers 7a and 7b of the boom cylinder assembly 7 with a reservoir 31.
  • a boom valve controlling hydraulic pilot valve 32 is provided on the upper vehicle body 3, and is here designed to be switched from its neutral position c to either an elongating position d or retracting position e by manipulating a lever 32a to feed pressure fluid either the first or the second pressure receiving portion 19a or 19b of the boom valve 19, thereby switching the boom valve 19 to either the elongating or the retracting position from its neutral position.
  • a service valve controlling hydraulic pilot valve 33 is also provided on the upper vehicle body 3 to operate in such a manner that if a pedal 34 is depressed a pressure fluid may be supplied from a service valve controlling pilot circuit 35 to the pressure receiving portion 22a of the service valve 22 to switch the service valve 22 to its fluid supply position for providing pressure fluid from the actuator port 27. It is seen that a pressure switch 36 is connected to the service valve controlling pilot circuit 35.
  • a selector switch 37 is provided also on the upper vehicle body 3, say, at the lever 32a of the boom valve controlling hydraulic pilot valve 32.
  • the selector switch 37 has a pair of switchable positions, i. e., the ramming position f and the breaking position g in order to issue a ramming command and a breaking command.
  • a pressure signal issued from the pressure switch and a ramming command issued from the selector switch are furnished or input to a timer relay 38.
  • the timer relay 38 is designed to electrically energize a solenoid 40 for a floating switching valve 39 a predetermined time interval after receipt of these signal or command inputs.
  • the floating switching valve 39 is provided in a floating pilot circuit 41 connected to the pressure receiving portion 30 of the float valve 29. It is normally held under a spring pressure at its drain position h and is adapted to be switched to its supply position i when the solenoid 40 is electrically energized.
  • a cylinder bore 43 which consists of a larger diameter cylinder bore 41 and a smaller diameter cylinder bore 42 and in which the piston 14 is slidably received.
  • the piston 14 is formed with a larger diameter section 45, a larger diameter rod section 46, an intermediate diameter rod section 47 and a smaller diameter rod section 48. It is also formed at both sides of the larger diameter section 45 with a first chamber 49 having a smaller pressure receiving area and a second chamber 50 having a larger pressure receiving area, with the addition of a subsidiary chamber 51, thereby together constituting a cylinder portion 52.
  • a servo valve 53 having a pump port 54, a principal port 55, a tank port 56 and a subsidiary port 57 and is so constructed that the pump port 54 may communicate with the first chamber 49 of the cylinder portion 52 and the valve 53 may be switched to a neutral position A , a first position B and a second position C as the piston 14 is displaced.
  • a principal switching valve 58 formed with a first, a second, a third and a fourth port 59, 60, 61 and 62, in which the first port 59 communicates with the circuit 28 shown in Fig. 1, the second port 60 communicates with the subsidiary port 57 of the servo valve 53, the third port 61 communicates with the reservoir 31 and the fourth port 62 communicates with the second chamber 50 of the cylinder portion 52.
  • the valve 58 also has a first pressure receiving portion 63 communicating with the principal port 55 of the servo valve 53 and a second pressure receiving portion 64 communicating with the above mentioned fluid circuit 28 which in turn communicates with both the first chamber 49 of the cylinder portion 52 and the pump port 54 of the servo valve 53.
  • the principal switching valve 58 is adapted to be switched to its first position D under a pressure applied to the first pressure receiving portion 63 and to its second position E under a pressure applied to the second pressure receiving portion 64.
  • the subsidiary chamber 51 of the cylinder portion 52 is adapted to communicate either with the reservoir 31 or with the second chamber 50 by means of a switching valve 70.
  • the switching valve 70 is of a pilot switching type in which it is held at its drain position F under a spring pressure and switched to a fluid communication position G under a fluid pressure applied to the pressure receiving position 71 that is connected to the floating pilot circuit 41.
  • the switching valve 70 may also be of a manually operated switching type provided with a mechanical detent feature.
  • the servo valve 53 will assume its second position C , thus establishing a fluid communication between the principal port 55 and the tank port 56 while blocking a fluid communication between the pump port 54 and the subsidiary port 57.
  • the principal switching valve 58 will be switched under the pressure in the second pressure receiving portion 64 to assume its second position E , thus establishing a fluid communication between the first port 59 and the fourth port 62 and a fluid communication between the second port 60 and the third port 61.
  • This will cause a pressure fluid to be supplied into the second chamber 50 of the cylinder portion 52 and will, with a pressure difference arising from a difference in area between the first chamber 49 and the second chamber 50, act to displace the piston 14 leftwards.
  • the servo valve 53 will assume its first position B , thus establishing a fluid communication between the pump port 54 and the principal port 55 while blocking a fluid communication between the tank port 56 and the subsidiary port 57. This will cause the pressure fluid to be delivered into the first pressure receiving portion 63 of the principal switching valve 58 to switch the latter to assume its second position D and will, for a reason as mentioned above, act to displace the piston 14 rightwards.
  • the switching valve 70 lies at the drain position F , blocking a fluid communication between the second chamber 50 and the subsidiary chamber 51 and causing the subsidiary chamber 51 to communicate with the reservoir 31, the chamber pressure receiving area required to displace the piston 14 leftwards can be seen to be equal to the pressure receiving area (A1-A2) of the second chamber 50, where A1 represents the cross sectional area of the larger diameter section 45 and A2 represents the cross sectional area of the intermediate diameter rod section 47.
  • the switched valve 70 will be switched to assume its position of communication G to establish a fluid communication between the second chamber 50 and the subsidiary chamber 51, the chamber pressure receiving area required to displace the piston 14 leftwards will be the sum of the second chamber (50) pressure receiving area (A1-A2) and the subsidiary chamber (51) pressure receiving area (A2-A3) where A3 is the cross sectional area of the smaller diameter rod section 48.
  • the body part 13 of the vibration generating unit 12 described hereinabove is formed with a tool insertion bore 72 continuously with the cylinder bore 43, as shown in Fig. 3.
  • the tool insertion bore 72 is adapted to accommodate either the breaker chisel 15 or the ramming tool 16, that is inserted therein.
  • a pin 73 is passed through a longitudinally elongated recess formed axially of the breaker chisel 15 or the ramming tool 16 to hold them interchangeably so that they when accepted may be capable of being reciprocated with a predetermined vibratory stroke amplitude.
  • a cap 74 is shown as detachably fitted in the tool insertion bore 73 and as retained by the pin 73 and as having a hook 75 suspended therefrom. This being the case, it is seen that if neither a breaking operation or a ramming operation is to be carried out, the cap 74 can be attached to the body portion 13 to fit in the tool insertion bore 73 so as to preclude introduction of a foreign matter. Then, the cap 74 can also be used to perform a suspending operation with the hook 75 attached thereto.
  • the breaker chisel 15 is fastened to the body part 13 of the vibration generating unit 12 and the selector switch 37 is set at the breaking position g .
  • the pedal 34 is depressed to operate the service valve controlling hydraulic pilot valve 33, thereby permitting a pressure fluid to be delivered into the service valve controlling pilot circuit 35. This will cause the pressure fluid to be delivered to the pressure receiving portion 22a of the service valve 22 which will then be set to assume its supply position, permitting a pressure fluid discharged from the hydraulic pump 18 to be supplied into the body position 13 of the vibration generating unit 12.
  • the piston 14 will then be reciprocated to periodically impact the breaker chisel 15 for initiating a breaking work.
  • the pressure switch 36 will issue a pressure signal whereas no ramming command or signal will be provided from the selector switch 37, thus holding the timer relay 38 inoperative.
  • the floating switching valve 39 will be held at its drain position h . Since no pressure fluid is then supplied to the floating pilot circuit 41, the switching valve 70 shown in Fig. 2 will remain set to assume its drain position F , thus accelerating the speed of reciprocation of the piston 14 to enhance the effect of the desired breaking work.
  • manipulating the lever 32a of the boom valve controlling hydraulic pilot valve 32 will cause the boom cylinder assembly 7 to perform its elongating and retracting operations, thus causing the boom member 6 to be vertically swung.
  • the ramming tool 16 is fastened to the body part 13 of the vibration generating unit 12 and the selector switch 37 is set at the breaking position f .
  • the service valve 22 will be set to take its supply position and the piston 14 in the vibration generating unit 12 will then commence reciprocating. Since the piston causes the ramming tool 16 to be vibrated, a desired ramming work will be initiated.
  • a pressure signal from the pressure switch 36 and a ramming command from the selector switch 37 will enter the timer relay 38.
  • the timer relay 38 will a predetermined time interval thereafter energize the solenoid 40 of the floating switching valve 39 to set the latter to assume its supply position i .
  • the boom member 6 comes capable of being vertically swung up and down with an external force, meaning that a desired ramming work can thereby be carried out with an enhanced efficiency.
  • a floating switch 80 is provided as attached to the lever 32a of the boom member controlling hydraulic pilot valve 32.
  • a shuttle valve 81 that is designed to detect a higher of pressures that act on the first and second pressure receiving portions 19a and 19b of the boom valve 19.
  • a pressure switch 82 is provided at the outlet side of the shuttle valve 81.
  • an ON signal from the float switch 80 and a pressure signal from the pressure switch are designed to enter the timer relay 38, which is operative to energize the solenoid 40 of the floating switching valve 39 in the presence of both an ON signal of the float switch 80 and a ramming command from the selector switch 37 which are received and yet in the absence of a pressure signal entered from the pressure switch 82.
  • the embodiment described may be modified to the extent, say, to omit the floating switch 80 and to allow the timer relay 38 to energize the solenoid 40 for the floating switching valve 39 only when a ramming command from the selector switch 37 is inputted but a pressure signal from the pressure switch 82 is not inputted. It can be readily appreciated that with such a modification as well, the same effects as mentioned above will be obtainable.
  • this embodiment makes an arrangement in which the boom valve 19 is assumed to take a float position x , and the boom member controlling hydraulic pilot valve 32 is provided with a detent mechanism.
  • the boom valve 19 is designed as capable of being switched to the float position x where the boom member controlling hydraulic pilot valve 32 is operated in a full stroke mode.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Architecture (AREA)
  • Shovels (AREA)
  • Operation Control Of Excavators (AREA)
  • Percussive Tools And Related Accessories (AREA)
  • Crushing And Grinding (AREA)
EP96933627A 1995-10-13 1996-10-11 Compresseur-concasseur Withdrawn EP0855468A4 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
JP265320/95 1995-10-13
JP7265320A JPH09111810A (ja) 1995-10-13 1995-10-13 転圧・ブレーカ作業機械
PCT/JP1996/002958 WO1997013925A1 (fr) 1995-10-13 1996-10-11 Compresseur-concasseur

Publications (2)

Publication Number Publication Date
EP0855468A1 true EP0855468A1 (fr) 1998-07-29
EP0855468A4 EP0855468A4 (fr) 2000-01-26

Family

ID=17415561

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96933627A Withdrawn EP0855468A4 (fr) 1995-10-13 1996-10-11 Compresseur-concasseur

Country Status (4)

Country Link
EP (1) EP0855468A4 (fr)
JP (1) JPH09111810A (fr)
KR (1) KR970021536A (fr)
WO (1) WO1997013925A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004092043A1 (fr) 2003-04-17 2004-10-28 Jozeph Maria Vermeulen Procede et dispositif de desarrimage d'une cargaison en vrac dans un navire par application de vibrations

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2337548B (en) * 1998-05-16 2002-02-20 Simon James Oliver Self-contained pavement crusher
JP4531303B2 (ja) * 2001-07-17 2010-08-25 古河機械金属株式会社 油圧ブレーカ
CN104005329B (zh) * 2014-06-10 2016-01-20 中铁工程机械研究设计院有限公司 一种振源恒压补偿系统
CN109382159B (zh) * 2018-12-18 2024-03-12 广西华银铝业有限公司 一种新型的圆锥破碎机臂架帽
CN111764246B (zh) * 2020-07-08 2022-05-17 山东公路机械厂有限公司 一种破碎夯实装置及包含该装置的破碎夯实一体机

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5169309U (fr) * 1974-11-11 1976-06-01
JPS6314653U (fr) * 1986-07-10 1988-01-30
JP3282895B2 (ja) * 1993-08-30 2002-05-20 株式会社小松製作所 ブレーカ内蔵式アーム付油圧ショベル

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
No further relevant documents disclosed *
See also references of WO9713925A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004092043A1 (fr) 2003-04-17 2004-10-28 Jozeph Maria Vermeulen Procede et dispositif de desarrimage d'une cargaison en vrac dans un navire par application de vibrations

Also Published As

Publication number Publication date
JPH09111810A (ja) 1997-04-28
WO1997013925A1 (fr) 1997-04-17
KR970021536A (ko) 1997-05-28
EP0855468A4 (fr) 2000-01-26

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