US3889405A - Excavator with teeth coupled for pivotal movement in opposite senses - Google Patents

Excavator with teeth coupled for pivotal movement in opposite senses Download PDF

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Publication number
US3889405A
US3889405A US463395A US46339574A US3889405A US 3889405 A US3889405 A US 3889405A US 463395 A US463395 A US 463395A US 46339574 A US46339574 A US 46339574A US 3889405 A US3889405 A US 3889405A
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US
United States
Prior art keywords
teeth
blade
distributor
fluid
tool according
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.)
Expired - Lifetime
Application number
US463395A
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English (en)
Inventor
Daniel G Ranini
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.)
Poclain SA
Original Assignee
Poclain SA
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Filing date
Publication date
Application filed by Poclain SA filed Critical Poclain SA
Application granted granted Critical
Publication of US3889405A publication Critical patent/US3889405A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • E02F9/20—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
    • 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
    • E02F3/36—Component parts
    • E02F3/40—Dippers; Buckets ; Grab devices, e.g. manufacturing processes for buckets, form, geometry or material of buckets
    • E02F3/402—Dippers; Buckets ; Grab devices, e.g. manufacturing processes for buckets, form, geometry or material of buckets with means for facilitating the loading thereof, e.g. conveyors
    • E02F3/405—Dippers; Buckets ; Grab devices, e.g. manufacturing processes for buckets, form, geometry or material of buckets with means for facilitating the loading thereof, e.g. conveyors using vibrating means
    • 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
    • Y10S37/00—Excavating
    • Y10S37/904—Vibration means for excavating tool

Definitions

  • the present invention relates to ground excavation penetration working tools.
  • Such excavation buckets require strong vibrating mechanisms which add to the weight of the bucket and also consume a large amount of power.
  • a ground penetration working tool comprising a blade intended to penetrate a mass of material, at least two teeth projecting from the blade, each said tooth being pivotable relative to the blade about an axis extending perpendicularly to the plane of the blade, coupling means for coupling the two teeth for synchronized pivotal movement in opposite senses, and actuating means operable to cause the teeth to pivot towards and away from one another.
  • an excavation bucket comprising a ground-engaging blade including two pivotal toothed members having teeth arranged to precede the blade as the blade enters the ground, means for constraining the teeth to make synchronous pivotal movements in opposite senses, and actuation means responsive to the deflection of the toothed members from mean positions about which they pivot to drive the members in the sense in which they have been deflected to the limit of their movement in that sense and thereafter to return the members to their mean positions.
  • the excavation bucket has a penetration blade 1 which forms an extension to one end of a generally C-shaped outer wall 2 of the bucket.
  • the blade 1 has two openings 3 each of which houses a corresponding body member 4 carrying a pair of teeth 5.
  • An arm 6 corresponding to each member 4 is pivoted on the wall 2 by means of a respective shaft 7; both shafts 7 being rigid with the wall 2.
  • Each shaft 7 is aligned with a corresponding one of the openings 3 in the blade 1 and is engaged by a forked portion 8 in the body member 4.
  • Each arm 6 is coupled to its corresponding body member 4 by means of a removable pin 9 which engages respective openings 10 and 11 in the body member 4 and the arm 6. In this manner, each arm 6 and its corresponding body member 4 are securely coupled together, the arm 6 forming the tail of the complete assembly and the body member 4 forming a removable part, which carries the wearing parts, namely the teeth 5.
  • Each opening 3 is delimited by upper 12 and lower 13 walls, which hold the body member 4 against motion in the vertical direction, and by two bosses 14 which limit the pivotal movement of each body member 4 in a horizontal plane.
  • a rod 16, of fixed length, is pivotally coupled at opposite ends thereof to corresponding arms 6 by means of respective shafts 17.
  • the two shafts 17 lie on opposite sides of a common plane containing the axis of the shafts 7 and are located at an equal distance from the plane 15.
  • a hydraulic double-action jack 18 is coupled at opposite ends thereof to the two arms 6, by means of two shafts 19.
  • a three-position distributor 20 is similarly coupled between the said arms 6, by means of two shafts 21.
  • the shafts 19 and the shafts 21 all lie on the same side of the plane 15; the two shafts l9 lying the same distance from the plane 15.
  • the shafts 19 both lie the same distance from the two shafts 21.
  • the distributor 20 has a slide portion which is coupled to one of the arms 6, and a body portion which is coupled to the other arm 6.
  • a removable metal portection sheet 22 covers the area of the shafts l9 and 21 and, consequently, the area of the jack l8 and of the distributor 20. This sheet has been omitted in FIG. 2, for the sake of clarity.
  • the hydraulic control system for controlling the jack 18 and the distributor 20 is shown in FIG. 3.
  • the system includes a two-position distributor 23, and a main pump 24 which is connected by a feed duct 25 to a fluid tank 26 and by an output duct 27 to the distributor 23.
  • a duct 28 connects the distributor 23 to the tank 26, while two ducts 29'and 30 connect the distributor 23 to the cylinder of the jack 18 on opposite sides of the piston which lies in the cylinder.
  • the chamber formed on one side of the piston will hereinafter be referred to as the large chamber 56 and the chamber formed on the other side of the piston will hereinafter be referred to as the small chamber 57, and is the chamber which contains the piston rod 31 of the jack 18.
  • Flexible hoses 32 and 33 are used to couple the ducts 29 and 30 to the chambers.
  • the hose 34 is connected to the output duct 38 of an auxiliary pump 39, which is connected to the tank 26 by its feed duct 40.
  • the duct is connected to the tank 26 by a duct 41.
  • the distributor 23 has two small guide ducts 42 and 43 which, are respectively connected to the flexible hoses 36 and 37 through ducts 44 and 45.
  • Ducts 46, 47 couple the feed tank 26 to respective ducts 44, 45.
  • the duct 46 includes an adjustable throttle and a non-return valve 48 which only allows fluid from the duct 44 to escape to the tank 26.
  • the duct 47 includes an adjustable throttle and a non-return valve 49 which allows fluid to pass through the duct only in the direction of from the duct 45 to the tank 26.
  • the three positions of the distributor 20 provide the following connections;
  • the two positions of the distributor 23 provide the following connections;
  • the distributor 23 in the first position, the distributor 23 establishes communication between the three ducts 27, 29 and 30, and blocks the duct 28;
  • the distributor 23 in the second position the distributor 23 establishes communication between the ducts 27 and 30, and between the ducts 28 and 29.
  • the output duct 38 of the pump 39 When distributor 20 is in its first position, the output duct 38 of the pump 39 is connected to the jack 43 (through ducts 34, 37 and 45). The effect of this is to move the distributor 23 in its first position.
  • the output duct 38 When the distributor 20 is in its second position, the output duct 38 is connected to the jack 42 (through ducts 34, 36 and 44), and this causes the distributor 23 to move into its second position. Accordingly, the first and second positions of the distributor 23 correspond respectively to the first and second positions of the distributor 20.
  • ducts 27 and 30 will be maintained in communication; the duct 30 being connected to the small chamber 57 of the jack 18 through the hose 33.
  • the pressurized fluid contained in this small chamber 57 acts on the piston in a sense to bring the ends of the arms 6 together and thus move the two pairs of teeth apart.
  • the large chamber 56 of the jack l8 communicates with the delivery duct 27 of the pump 24 when the dis tributor 23 is in its first position, and with the tank 26 (through duct 28) when the distributor 23 is in the second position.
  • the pressurized fluid contained in the large chamber 56 acts on the piston to drive the ends of the two arms 6 apart.
  • each of the pairs of teeth 5 will tend to insert themselves into the gaps in the ground which form points of least resistance, even in the absence of hard spots.
  • the reaction of the ground on one of the pairs of teeth 5 is on an average equal to and opposite in direction to that which the ground exerts on the other tooth 5.
  • the ground forces act on the teeth in the same sense as the coupling between the two pairs of teeth allow them to move together.
  • the material is therefore, either divided by the external side edges of the pairs of teeth 5, or on the contrary pinched between the internal side edges of the pairs of teeth.
  • the stresses acting on the teeth are taken up, eitherby the shafts 7 and 17, and/or by the bosses 14.
  • the penetration forces of the bucket do not therefore, on the average, cause any lateral deflection of said bucket.
  • the function and action of the jack l8 and of its bydraulic control circuit will now be considered.
  • the hydraulic system described is unstable since the large chamber 56 is permanently connected, either to the tank 26, or to the output duct 27 of the pump24.
  • the jack 18 tends, either to retract under the action of the pressure of fluid in the small chamber 57, or to be extended under the action of pressure of fluid in the large chamber 56. Accordingly the relative positions of the arms 6 will vary and the pairs of teeth 5 will perform a movement producing a see-saw effect.
  • the seesaw effect disintegrates the material, which makes the penetration of the teeth 5, even easier.
  • the adjustable throttles 50 and 51 act to prevent the pressurized fluid fed by the pump 39 into one of the two jacks 42, 43, from returning to the tank 26 before having acted on the said jack, and act to resist the pressure of fluid from the other jack from which fluid is being emptied.
  • These restrictions provided by the throttles create a damping effect on the distributor 23 and this damping effect is consequently transmitted to act on the movement of the teeth 5.
  • the value of this damping effect can be adjusted by adjusting the throttles.
  • the above described excavation bucket has been found to suppress or, at least, provide a substantial decrease in the effect of shocks applied to the teeth 5 on the remainder of the machine.
  • the mechanisms (the hingeing shafts, and other members) are therefore subjected to smaller stresses, and the driver of the machine can work with greater comfort.
  • the described excavation bucket requires smaller operating jacks than previously proposed buckets to provide the same penetration. Accordingly, the jacks employed can be lighter and, additionally, the payload of carried material can be greater than that of standard buckets.
  • This energy is not a vibration energy (low beat frequency), and is applied to parts having low mass (teeth 5).
  • actuating means connected to the teeth and operable to cause the teeth to pivot towards and away from one another
  • said actuating means includes a single driving element coupled to the said two teeth at points lying on the same side of a common plane containing the said pivotal axes of the two teeth, and wherein the coupling means comprises a rod of constant length pivotally coupled to the two teeth at two points lying on opposite sides of said plane.
  • actuating means comprises a hydraulic jack.
  • each tooth comprises a tail portion which is pivoted on the penetration blade and which portion is coupled to the actuating means
  • a wearing part which constitutes the working part of the tooth and is detachably secured to the said tail portion.
  • actuating means comprises a main source of pressurized fluid
  • the said single driving member comprising a piston member
  • a cylinder having a fluid admission chamber for receiving fluid under pressure to drive the piston member from a first to a second position
  • a two-position distributor which selectively provides the admission chamber with communication with said main source when in one position and with the tank when in the other position, and
  • an oscillator which is coupled to the distributor to cause the driving member to pivot the teeth in a sense towards the mean positions about which they pivot.
  • the oscillator comprises an auxiliary source of pressurized fluid, first and second fluid-operated drive members respectively operable to drive the two position distributor into said one position and the said other position, and
  • a three-position distributor which is coupled to both teeth, and is movable to change into a corresponding one of three positions in response to movement of the teeth, the three-position distributor when in the first and second of its three positions respectively supplying fluid from the auxiliary source to the first and second fluid-operated drive members and when in its intermediate position, isolating both first and second drive members from the auxiliary source.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Operation Control Of Excavators (AREA)
  • Earth Drilling (AREA)
  • Shovels (AREA)
  • Component Parts Of Construction Machinery (AREA)
US463395A 1973-05-15 1974-04-23 Excavator with teeth coupled for pivotal movement in opposite senses Expired - Lifetime US3889405A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR7317566A FR2229822A1 (fr) 1973-05-15 1973-05-15

Publications (1)

Publication Number Publication Date
US3889405A true US3889405A (en) 1975-06-17

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ID=9119360

Family Applications (1)

Application Number Title Priority Date Filing Date
US463395A Expired - Lifetime US3889405A (en) 1973-05-15 1974-04-23 Excavator with teeth coupled for pivotal movement in opposite senses

Country Status (10)

Country Link
US (1) US3889405A (fr)
JP (1) JPS5019204A (fr)
AR (1) AR200320A1 (fr)
BE (1) BE815008A (fr)
BR (1) BR7403745D0 (fr)
CA (1) CA1001685A (fr)
DE (1) DE2422826A1 (fr)
FR (1) FR2229822A1 (fr)
GB (1) GB1435631A (fr)
IT (1) IT1014114B (fr)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4132017A (en) * 1976-08-13 1979-01-02 National Research Development Corporation Blade for earth moving equipment
US4403430A (en) * 1979-10-22 1983-09-13 Matisa Materiel Industriel S.A. Plough with lateral ejectors for displacing railway track ballast
US4704812A (en) * 1986-07-22 1987-11-10 Paramore Jr Alvie R Scraper pan with cutting blade
US5426875A (en) * 1994-04-18 1995-06-27 Pengo Corporation Reversible tooth with adjustable attack angle
US5794714A (en) * 1997-04-29 1998-08-18 Brown; Dennis Finish dirt scraper
US20170037596A1 (en) * 2015-08-04 2017-02-09 Lowell Underwood Excavator Bucket With an Internally Deployable Breaker

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2811681C2 (de) * 1978-03-17 1986-10-09 Gewerkschaft Eisenhütte Westfalia GmbH, 4670 Lünen Ladeschaufel, insbesondere für Seitenkipplader
JPH0739968Y2 (ja) * 1989-12-18 1995-09-13 新キャタピラー三菱株式会社 振動バケット
FR3107288B1 (fr) * 2020-02-19 2022-01-07 Db Ind Brevet d’invention pour un dispositif de dents dynamiques pour bennes preneuses, poches de forage et godets sur engins de chantier

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1878037A (en) * 1929-04-08 1932-09-20 Goodman Mfg Co Loading machine
US3145488A (en) * 1962-12-26 1964-08-25 Deere & Co Vibrating bucket
US3627056A (en) * 1968-12-23 1971-12-14 Thelmer A Rogers Vibrating plow with balanced forces

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1878037A (en) * 1929-04-08 1932-09-20 Goodman Mfg Co Loading machine
US3145488A (en) * 1962-12-26 1964-08-25 Deere & Co Vibrating bucket
US3627056A (en) * 1968-12-23 1971-12-14 Thelmer A Rogers Vibrating plow with balanced forces

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4132017A (en) * 1976-08-13 1979-01-02 National Research Development Corporation Blade for earth moving equipment
US4403430A (en) * 1979-10-22 1983-09-13 Matisa Materiel Industriel S.A. Plough with lateral ejectors for displacing railway track ballast
US4704812A (en) * 1986-07-22 1987-11-10 Paramore Jr Alvie R Scraper pan with cutting blade
US5426875A (en) * 1994-04-18 1995-06-27 Pengo Corporation Reversible tooth with adjustable attack angle
US5794714A (en) * 1997-04-29 1998-08-18 Brown; Dennis Finish dirt scraper
US20170037596A1 (en) * 2015-08-04 2017-02-09 Lowell Underwood Excavator Bucket With an Internally Deployable Breaker

Also Published As

Publication number Publication date
IT1014114B (it) 1977-04-20
JPS5019204A (fr) 1975-02-28
FR2229822A1 (fr) 1974-12-13
GB1435631A (en) 1976-05-12
AR200320A1 (es) 1974-10-31
CA1001685A (en) 1976-12-14
BR7403745D0 (pt) 1974-12-31
BE815008A (fr) 1974-09-02
DE2422826A1 (de) 1974-12-05

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