US3600957A - Oscillating power unit - Google Patents

Oscillating power unit Download PDF

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Publication number
US3600957A
US3600957A US859089A US3600957DA US3600957A US 3600957 A US3600957 A US 3600957A US 859089 A US859089 A US 859089A US 3600957D A US3600957D A US 3600957DA US 3600957 A US3600957 A US 3600957A
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US
United States
Prior art keywords
oscillator
eccentric
power unit
drive shaft
lobe
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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
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US859089A
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English (en)
Inventor
Olly O Stoffel
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.)
STOFFEL ENGINEERING CORP
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STOFFEL ENGINEERING CORP
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B02—CRUSHING, PULVERISING, OR DISINTEGRATING; PREPARATORY TREATMENT OF GRAIN FOR MILLING
    • B02C—CRUSHING, PULVERISING, OR DISINTEGRATING IN GENERAL; MILLING GRAIN
    • B02C19/00—Other disintegrating devices or methods
    • B02C19/16—Mills provided with vibrators
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
    • B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
    • B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
    • B06B1/162—Making use of masses with adjustable amount of eccentricity
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/1836—Rotary to rotary
    • Y10T74/18392—Crank, pitman, and crank
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18544—Rotary to gyratory
    • Y10T74/18552—Unbalanced weight
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/211—Eccentric
    • Y10T74/2116—Eccentric having anti-friction means, e.g., roller bearing, lubrication, etc.

Definitions

  • Brown ABSTRACT An oscillating power unit for use with a variety of tools and equipment that are vibrated in their operation.
  • An inertial mass rocking about a fixed pivot is driven by an orbital motion eccentric mechanism in such a manner that the effective power is concentrated along one axis of motion and minimized in all other directions.
  • the eccentric drive has a variable throw that is easily adjusted to selectively vary the oscillating power output when the unit is installed in an operating assembly without dismantling the structure, although all moving parts except the drive shaft are fully enclosed.
  • PATENTEUAUBZMQH 3.600857 sum 1 OF 5 INVIiNTUR. OLLY O. STOFFEL ATTORNEY PATENTEU AUB24
  • Some vibrators have used dual inertial masses that are synchronized to work together in one direction and oppose each other in other directions. These are cumbersome for the power developed and they do not entirely solve the problem. Furthermore, the power output of such vibrators is usually difficult or impossible to adjust without dismantling the apparatus, and the speed or pulse rate is often the only reasonably, adjustable variable.
  • the oscillating power unit has an inertial mass oscillator mounted for a rocking action in the plane of useful power output, and is driven by an orbital eccentric mechanism in such a manner that maximum power is produced along one axis and force moments in other directions are minimized. All moving parts except an extending drive shaft are fully enclosed in a compact casing and the unit is readily adaptable to various tools and machines requiring a controlled vibratory action.
  • the power output is also adjustable by varying the eccentric stroke. This is easily accomplished through conveniently located access in the casing, without dismantling the unit or disturbing its mounting.
  • the orbital eccentric mechanism has means for translating rotation of a drive shaft to reciprocating, linear pivotal movement of the eccentric mechanism within the inertial mass, that moves the oscillator mass in a reciprocating, rocking, movement about a fixed offset pivot.
  • the internal forces between the eccentric mechanism and the oscillator mass in translating force from the shaft to the oscillator mass creates reciprocating force moments along a given axis, and absorbs force moments in other directions.
  • the amount of force generated is selectively set by rotatably positioning one eccentric member within another eccentric member within the eccentric mechanism. This allows selective setting of the throw of the eccentric mechanism and the rocking movement of the oscillator and thus selective setting of the oscillating force generated.
  • FIG. I is a side elevation of an embodiment of the invention.
  • FIG. 2 is an illustration of a typical use of an embodiment of the invention.
  • FIG. 3 is an enlarged sectional view taken on line 33 of FIG. 1.
  • FIG. 4 is a sectional view taken on line 44 of FIG. 3.
  • FIG. 6a to 60 show three different adjustments of eccentric throw in diagrammatic form.
  • FIGS. 7a to 7f are diagrams of six positions of the mechanism through one complete cycle of operation.
  • the power unit is contained in a cylindrical casing 10 enclosed by end plates 12 and mounted on a base frame 14 for convenience of attachment to various apparatus by any known suitable means.
  • the frame 14 comprises a base plate 16 and a pair of arcuate saddle members 18 in which casing 10 is seated, but the configuration may vary according to specific use.
  • a substantially discoid inertial weight element or oscillator 20 that is pivoted near its lower edge on a rocker pin or shaft 22 extending across the casing 10 parallel to the axis of the cylindrical casing.
  • the oscillator 20 is smaller than the interior of casing 10 to allow clearance for a rocking motion and is slightly elongated in a direction radial to pin 22. This minimizes clearance at the top and bottom while allowing sufficient clearance at the sides.
  • a large void opening 24 that is elongated horizontally and extends axially through the complete thickness of the oscillator 20. Fixed in the opposite ends of opening 24 are vertical wear plates 26 with parallel opposed faces.
  • rocker pin 22 The opposite ends of rocker pin 22 are held in sockets 28 of cap members 30 which are inset in openings in the end plates 12 as illustrated in FIG. 3.
  • the cap members 30 are secured to the end plates 12 by bolts 94 and cap screws 32 close threaded openings through which studs are inserted to facilitate removal of the cap members 30.
  • a generally avoid slide block 36 Mounted in the opening 24 is a generally avoid slide block 36, with side plates 38 fixed to opposite ends to slide smoothly on wear plats 26.
  • a large circular bore 40 containing axially positioned roller bearings 42 with bearing races 43.
  • Mounted in the bearings 42 is an eccentric drive block 44.
  • the drive block 44 is split longitudinally on a vertical plane into two portions designated 44a and 44b, which are connected by axially extending, circumferentially spaced bolts 46.
  • the heads 47 of bolts 46 abut against the opening in portion 44a and the threaded ends 49 engage the portion 44b.
  • the heads 47 have known socket springs 48 retained in opposed sockets 50 between the two drive block portions, as illustrated in FIG. 3.
  • guide plates 52 are inset in oscillator 20 along opposite ends of wear plates 26, and project inwardly over the ends of slide plates 38.
  • Drive block 44 is driven by a drive shaft 54 extending axially through casing 10, the ends being journaled in suitable bearings 56.
  • the bearings 56 are held in bearing plates which, for purposes of description, are designated front bearing plate 58 and back bearing plate 60, inset in and secured to end plates 12 by bolts 95.
  • front bearing plate 58 In the front bearing plate 58 are set screws 62 that engage and apply axial load to the bearing therein, to eliminate axial play.
  • Drive shaft 54 has an eccentrically enlarged central lobe 64 with tappered cylindrical shoulders 66 and reduced end portions 68.
  • Drive blocks 44a and 44b have eccentrically offset bores 70 shaped to fit closely on the lobe 64 and shoulders 66, so that clamp bolts 46 can be tightened to lock the drive block portions on the tapered shoulders with a jamming action for a positive drive connectron.
  • the aligned openings 71 in the drive blocks 44a and 44b are offset from the axis of the drive shaft 54.
  • the upper radial thickness of the drive blocks is greater than the lower radial thickness.
  • the center of the enlarged central lobe 64 is offset from the axis of the shaft 54. Since the shaft 54 is rotatable within openings 71, the offset openings 71 and the central lobe 64 form an eccentric positioning of the two masses, which eccentric positioning is adjustable. Such adjustment allows the total mass of the two members, the lobe 64 and the drive blocks 44, and their radial displacement relative to the drive shaft axis to be selectively set, thus providing for selectively setting the throw or strape of the eccentric mechanism.
  • the drive assembly thus comprises an eccentric within an eccentric and is easily adjusted to vary the stroke.
  • an indexing pin 74 is mounted on front bearing plate 58 and is biased by a spring 76 to seat into a radial slot 78 in drive block 44a.
  • Indexing pin 74 has an enlarged head 80 with web portions 82 which normally rest in shallow grooves 84 in a boss 86 projecting from the bearing plate coaxial with the pin. In this position the indexing pin is held clear of slot 78, as in FIG. 3.
  • the pin is turned 90 so that the web portions 82 can drop into deep grooves 88 in boss 86, allowing the pin 74 to enter the slot.
  • the clamp bolts 46 are loosened and separator springs 48 push the drive block portions apart.
  • pin 74 is secured to end plate 12, the locked pin also holds the drive blocks 44 in the illustrated position.
  • drive shaft 54 can be rotated relative to the drive blocks 44, changing the eccentric relation of lobe 64 to the eccentricity of bores 70.
  • the drive shaft 54 has a slot 57 in the end thereof, which slot may be used to calibrate the position of the two eccentrics and thus the throw or stroke of the oscillator. However other suitable and more precise calibration markings may be used.
  • the slot 78 has a vertical extension to allow for slight vertical movement of the drive blocks 44 that occurs as a result of relative rotational movement between the two eccentrics.
  • the clamp bolts are tightened to lock the assembly and the access plugs 72 are replaced and indexing pin 74 is withdrawn and locked out.
  • FIGS. 6a, 6b and 6c show three different eccentric positions.
  • a reference marker 90 is used on drive block 44 and a reference marker 92 on lobe 64 to clarify the positions.
  • the assembly is set for maximum throw T, with both reference markers radially aligned.
  • the axial center of shaft 54 is at point 91
  • the axial center of the assembly is at 93
  • the axial center of lobe 64 is at 61.
  • the radial throw of the double eccentric mechanism is the throw T. This represents the distance that the oscillator 20 will be rocked in each direction and also determines the relative up and down and sideward movement of the drive blocks 44, and thus the slide block 36.
  • This maximum throw position is also illustrated in FIGS.
  • FIG. 6b shaft 54 is rotated 90 and the eccentrics are at an intermediate position, with the displacement between center points 91 and 93 giving a reduced throw of T1.
  • FIG. 6c illustrates the markers 90 and 92 substantially opposed with the throw T2 reduced to zero. It may be understood that in this position, the eccentric of the lobe 64 exactly equals the eccentric of the drive blocks 44. Thus the two eccentrics exactly equal each other and the center of the mass and throw 93 is on the axis of the drive shaft 54. Thus rotation of the drive shaft 54 rotates the drive block 44 without imparting rocking motion to the oscillator 20.
  • the oscillator 20 has oil passages 101 and side oil passages 105, the slide block 36 has oil passages 103 and the bearing races 43 have oil passages 107.
  • the oil in the unit is normally carried at a level illustrated by dotted lines 111.
  • the oscillator 20 in its rocking movement, drives oil upward through openings 105 and 101 and around the outer surface 113 to the upper space between the oscillator 20 and the slide block 36.
  • the oil then passes through the upper oil holes 101 to the slide block 36 and also flows down the outer surface of the oscillator 20.
  • the slide block 36 in the up and down movement contacts the oil and moves it upwardly through lower holes 103 as well as passing oil through upper holes 103 to the bearings 42 through holes 105.
  • Oil also moves through upper holes 101 and over the outer surface of the slide block 36 to the bearings surfaces between plates 26, 38 and 52.
  • Pin 22 having oil grooves 34 receives oil through holes 101.
  • the oil may be inserted into the system through the upper valve 109 and hole 107.
  • Valve 109 may be an appropriate pressure set check valve to release pressure buildup or equalize pressure in the internal volume of the oscillating power unit.
  • the oil level 1 11 is sufficient to provide oil to the rotating drive blocks.44 when the eccentric members are set for zero throw.
  • the spacing between the surface 115 of the oscillator 20 and the inner surfaces of the end plates. 12 is sufficient to pass oil to the bearings 56. Also the surfaces 115 of the oscillator 20 have oil grooves (not shown) to provide controlled oil flow between the adjacent surfaces of the oscillator 20 and the end plates 12. Known seals 49, prevent oil leaks around the drive shaft 54.
  • a suitable power source is connected to the drive shaft 54.
  • the eccentric mechanism is then set for the desired amount of throw in the manner previously described.
  • the drive shaft 54 is then rotated, rotating the drive blocks 44 in bearings 42. Since there is an offset of the combination drive lobe 64 and the drive blocks 44, the slide block 36 is moved sideways and up and down. This movement causes the slide block 36 to slide vertically relative to the oscillator 20 and to move the oscillator in a reciprocating, rocking movement around pin 22. This movement is illustrated in FIGS. 7a to 7f, with the drive blocks 44 movement illustrated in 60 increments of clockwise rotation.
  • the rotation center of axis of drive shaft 54 is indicated by circle 98, with the particular location of the throw of the lobe 64 and drive blocks 44 being indicated by numeral 65.
  • the eccentric mechanism has the throw in the upward vertical position and the slide block 36 at the top of its stroke.
  • the slide block 36 is moved to the right and downwardly. This pivots the oscillator 20 to the right.
  • the slide bearing block and the oscillator 20 moves to the right to the maximum extent for the given eccentric setting.
  • the slide block 36 moves downward, it also moves back toward the center position pulling the oscillator 20 from the maximum throw to the right.
  • the drive shaft 54 in its rotational movement moves the slide block 36 to the downward position illustrated in FIG. 7d and then continues in movement to the left in the same manner as previously described in the movement to the right.
  • the slide block moves vertically with side movements generally defining a circular movement corresponding to the circular movement of the lobe 64 and drive blocks 44.
  • the oscillator power unit provides force moments only in substantially the horizontal direction, which is in the direction of arrows 151 and 153.
  • the slide block 36 has a vertical component of motion, there is almost no vertical oscillation force produced in the unit.
  • the inertia of the slide block 36 is added to the inertia of the oscillator 20, the latter being effective about the axis of rocker pin 22 and thus has a long lever arm.
  • the mass of the slide block 36, including the drive blocks 44 and lobe 64, is only a part of the moving assembly and is effective over a smaller lever arm than the whole mass.
  • the energy of the slide block 36 is applied to the weight element through the sliding members 26 and 38, which are inclined to vertical throughout most of the cycle of oscillation. Due to the shallow angle of inclination, as will be apparent in FIGS. 7b, 7c, 72 and 7f the energy of the driven slide block 36 is absorbed in imparting a lateral motion to the oscillator 20.
  • the slide block mass passes downward through the midpoint of the mechanism, the slide block is exerting force against the oscillator 20 to reverse the rocking movement of the oscillator 20.
  • the vertical force component of the sliding block is absorbed in moving the oscillator 20 and the horizontal throw of the mass provides the horizontal force components.
  • the component to be vibrated is usually mounted for motion in a particular plane or along a single axis. If the vibrating mechanism has an effect in a direction other than that desired, the structure must be strengthen to withstand the stress which is not always practical. With the present unit such reinforcement is unnecessary.
  • a typical use of the unit is illustrated in simple form in FIG. 2.
  • the complete oscillating power unit 100 is mounted on top of a ripper device having a shank 102 carrying a working tooth 104, or similar ripping structure.
  • the shank 102 is pivotally attached to a frame support 106 to swing from front to rear, as indicated by the directional arrows.
  • the frame has tow bar means 108 for attachment to a vehicle, the power unit being operated as the assembly is towed with the working shank 102 below ground so that the vibration eases penetration.
  • suitable motor or power source may be used to drive the unit.
  • the adjustable throw of the eccentric mechanism makes it possible to control the power output without changing speed, which is an advantage with apparatus having frequency or resonance limitations. Such adjustment can be made as described above without dismantling or removing the unit from the associated apparatus.
  • the rocking action of the oscillator 20 and sliding of the slide block 36 provide effective pumping action to circulate lubricant with the unit.
  • the oil level may be selectively changed to conform, as desired, to different amounts of eccentric throw or vertical movement of the slide block. Because of the compactness and low inertia of the eccentric mechanism itself, the unit is capable of very rapid starting and stopping and the inertia of the oscillator 20 acts as a brake by applying pressure to the slide block when driving power is shut off causing the slide block and power shaft to stop substantially instantly.
  • An oscillating power unit comprising:
  • rocker pin fixed in said casing substantially parallel to and radially offset from said drive shaft
  • said drive means include an eccentric lobe on said drive shaft
  • said weight element has a slide block mounted therein for sliding motion substantially radial to said rocker pin, said drive block being rotatably held in said slide block.
  • said drive block has clamp means adjustably securing it to said drive shaft.
  • said lobe has axially tapered portions, said drive block being in two axially separated elements seating on said tapered portions with clamp means securing the separated elements together.
  • one of said end plates has removable elements exposing said clamp means.
  • indexing means on said casing selectively engageable with said drive block in one position in which said clamp means are aligned with said removable elements.
  • An oscillating power unit comprising: an oscillator pivotally supported at one side for radial rockin movement around the pivot, said oscllator having a rotatable eccentric means positioned within said oscillator and enclosed thereby and spaced radially from said pivot for providing an orbital movement with a rotating eccentric throw, and said eccentric means has a linear sliding drive connections with said oscillator and within said oscillator for translating said orbital movement to reciprocating, radial rocking movement of said oscillator on said pivot.
  • said eccentric means and said pivot each have an axis of rotation, which are parallel and are in the same plane.
  • An oscillating power unit as claimed in claim 9 in which: said oscillator has an opening with opposite linear sides, said sides are parallel with said plane, and an open space between the upper and lower edges of said eccentric means and said oscillator opening allowing linear movement of said eccentric means in said oscillator opening.
  • An oscillating power unit as claimed in claim 10 in which:
  • said eccentric means has a body with a pair of sides for slidably contacting said sides in said opening, said body has a circular opening with a cylindrical member rotatably positioned therein, and drive shaft means for rotating said cylindrical member having an axis of rotation offset from the axis of said cylindrical member.
  • said drive shaft means includes a drive shaft with an enlarged cylindrical lobe, the axis of which is offset from the axis of said drive shaft, said lobe is rotatable in said body, and means for fixing said cylindrical member to said lobe at given rotational positions therebetween, whereby the eccentric throw of said lobe may be selectively adjusted.
  • oscillator has a cylindrical shape with flat end surfaces, a frame for supporting said pivot having flat ends adjacent said flat ends surfaces and a housing having a cylindrical opening for enclosing said oscillator, and said oscillator having oil passages through to said opening at the top and bottom thereof.
  • An oscillating power unit as claimed in claim 13 in which:
  • said cylindrical member has a radial slot in the surface adjacent one of said flat ends, and releasable pin means in said one of said flat ends for selectively projecting into said slot and maintaining orientation of said cylindrical member upon rotation of said lobe.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Food Science & Technology (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
US859089A 1969-09-18 1969-09-18 Oscillating power unit Expired - Lifetime US3600957A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US85908969A 1969-09-18 1969-09-18

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US3600957A true US3600957A (en) 1971-08-24

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Application Number Title Priority Date Filing Date
US859089A Expired - Lifetime US3600957A (en) 1969-09-18 1969-09-18 Oscillating power unit

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US (1) US3600957A (de)
JP (1) JPS496849B1 (de)
CA (1) CA921290A (de)
DE (1) DE2046215C3 (de)
ZA (1) ZA706360B (de)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3866480A (en) * 1972-06-02 1975-02-18 Martin Concrete Eng Co Orbital vibrator
US4041844A (en) * 1974-06-12 1977-08-16 Sulzer Brothers Limited Hydrostatic piston machine
US4041800A (en) * 1975-04-07 1977-08-16 Nikkiso Co., Ltd. Stroke length adjusting devices
EP0302152A1 (de) * 1987-08-05 1989-02-08 Conoco Inc. Vibrator mit orbital oszillierender Masse
US4817417A (en) * 1987-05-06 1989-04-04 Westinghouse Electric Corp. Double eccentric mount
US4899616A (en) * 1987-12-29 1990-02-13 Sankyo Manufacturing Company, Ltd. Press with stroke control device
US4907456A (en) * 1988-03-24 1990-03-13 Westinghouse Electric Corp. Sensor probe system
US4914977A (en) * 1987-12-29 1990-04-10 Sankyo Manufacturing Company, Ltd. Stroke control device for use in press
NL2000741C2 (nl) * 2007-07-10 2009-01-13 F En P Beheer B V Trilblok.
US20160009386A1 (en) * 2013-03-20 2016-01-14 Lord Corporation Low moment force generator devices and methods

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4709362A (en) * 1985-09-27 1987-11-24 Conoco Inc. Oscillating orbital vibrator
DE29805619U1 (de) * 1998-03-27 1999-07-29 Passavant-Werke Ag, 65326 Aarbergen Vibrations-Verdichtungssystem zum Verdichten von Formmassen in Formkästen
CN103551297B (zh) * 2013-11-18 2015-09-23 农业部规划设计研究院 一种振幅可调式激振装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2335645A (en) * 1941-12-08 1943-11-30 Scintilla Ltd Variable crank gear
US2592237A (en) * 1950-01-11 1952-04-08 Builders Iron Foundry Pump stroke adjusting device
US2776573A (en) * 1954-03-01 1957-01-08 Baldwin Lima Hamilton Corp Variable reciprocating stroke mechanism
US2947183A (en) * 1957-09-30 1960-08-02 Chain Belt Co Vibration imparting mechanism
US3189106A (en) * 1962-01-09 1965-06-15 Jr Albert G Bodine Sonic pile driver

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2335645A (en) * 1941-12-08 1943-11-30 Scintilla Ltd Variable crank gear
US2592237A (en) * 1950-01-11 1952-04-08 Builders Iron Foundry Pump stroke adjusting device
US2776573A (en) * 1954-03-01 1957-01-08 Baldwin Lima Hamilton Corp Variable reciprocating stroke mechanism
US2947183A (en) * 1957-09-30 1960-08-02 Chain Belt Co Vibration imparting mechanism
US3189106A (en) * 1962-01-09 1965-06-15 Jr Albert G Bodine Sonic pile driver

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3866480A (en) * 1972-06-02 1975-02-18 Martin Concrete Eng Co Orbital vibrator
US4041844A (en) * 1974-06-12 1977-08-16 Sulzer Brothers Limited Hydrostatic piston machine
US4041800A (en) * 1975-04-07 1977-08-16 Nikkiso Co., Ltd. Stroke length adjusting devices
US4817417A (en) * 1987-05-06 1989-04-04 Westinghouse Electric Corp. Double eccentric mount
EP0302152A1 (de) * 1987-08-05 1989-02-08 Conoco Inc. Vibrator mit orbital oszillierender Masse
US4899616A (en) * 1987-12-29 1990-02-13 Sankyo Manufacturing Company, Ltd. Press with stroke control device
US4914977A (en) * 1987-12-29 1990-04-10 Sankyo Manufacturing Company, Ltd. Stroke control device for use in press
US4907456A (en) * 1988-03-24 1990-03-13 Westinghouse Electric Corp. Sensor probe system
NL2000741C2 (nl) * 2007-07-10 2009-01-13 F En P Beheer B V Trilblok.
US20160009386A1 (en) * 2013-03-20 2016-01-14 Lord Corporation Low moment force generator devices and methods

Also Published As

Publication number Publication date
DE2046215A1 (de) 1971-04-15
JPS496849B1 (de) 1974-02-16
DE2046215B2 (de) 1979-05-10
CA921290A (en) 1973-02-20
ZA706360B (en) 1971-05-27
DE2046215C3 (de) 1980-01-10

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