US3460808A - Apparatus and method for generating vibrations - Google Patents

Apparatus and method for generating vibrations Download PDF

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Publication number
US3460808A
US3460808A US559904A US3460808DA US3460808A US 3460808 A US3460808 A US 3460808A US 559904 A US559904 A US 559904A US 3460808D A US3460808D A US 3460808DA US 3460808 A US3460808 A US 3460808A
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Prior art keywords
fluid
core
inertia ring
ring
blade
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Robert L Wilde
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ARROW MASTER INCORPORATED A CORP OF ILLINOIS
Koehring Co
Dart Mfg and Sales Co
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Dart Mfg and Sales Co
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    • 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
    • B06B1/18—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid
    • B06B1/186—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid operating with rotary unbalanced masses
    • 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

Definitions

  • the means for moving the ring orbitally relative to the member includes means for supplying to the motor cavity, during at least approximately one-half of each cycle, a predetermined amount of fluid of substantially constant pressure without substantially any linear mass velocity, the volume of fluid equaling the instantaneous volume of the motor cavity whereby the increase volume of fluid, to be disposed within the motor cavity, occurring from expansion of the fluid substantially equals the increased volume of the motor cavity during movement of the ring.
  • the means for moving the ring orbitally relative to the member also includes means for effecting at least a partial decompression of the motor cavity and exhausting the exhaust cavity.
  • This invention lies in the field of vibration generators such as those used in compacting freshly poured concrete and operating shaking machines of various types but is not limited thereto. It is directed particularly to the type of apparatus in which a component of substantial mass is moved in an orbital path with respect to the balance of the apparatus to produce alternating force resultants in opposite directions. More specifically it is directed to the type of vibrator in which an inertia ring is caused to gyrate about a central core in an orbital path, using compressed fluid as the power source.
  • Devices of the type mentioned above are generally classed as rotary vibrators because in fact the unbalanced weight component has an axle which is mounted in hearings to allow rotation of the component, or the component actually rolls around a track of some kind.
  • a solid or hollow cylindrical Weight rolls in contact with the inner wall of a cylinder of larger diameter.
  • a hollow cylindrical Weight in the form of a ring rolls in contact with a core having a diameter less than the inside diameter of the ring.
  • the present invention overcomes the disadvantages mentioned above by providing an apparatus which operates on the same broad principles as other inertia ring types but which encounters a minimum of wear by using the pressure fluid as a lubricant and as a natural mass preventing direct physical contact between the moving inertia ring and the stationary supporting member.
  • the extent and timing of the opening of the inlet and outlet ports is such as to insure entry of the proper amount of working fluid in each cycle and adequate provision for exhausting the fluid at the proper time in the sequence. Moreover this is accomplished with a minimum of complexity, there being only two moving parts in the as sembly.
  • the apparatus comprises a spool-shaped supporting member having a central cylindrical core and a pair of laterally extending end walls defining a cylindrical work chamber.
  • a spool-shaped supporting member having a central cylindrical core and a pair of laterally extending end walls defining a cylindrical work chamber.
  • An inertia ring is mounted in the work chamber for free oscillatory movement in any direction radial of the core.
  • the inner diameter of the inertia ring is substantially larger than the diameter of the core, and the length of the ring is slightly less than the longitudinal distance between the inner faces of the end walls.
  • the ring can gyrate about the core, following an orbital path, and produce centrifugal force successively in all directions radial of the core, the force being transmitted to the core and its associated elements through the medium of the mass of compressed fluid, which then apply the force externally for useful purposes such as compacting freshly poured concrete.
  • a guide slot is formed in the core extending longitudinally between the end walls and extending radially from a location near the axis of the core to the surface of the core.
  • a barrier blade is mounted in the slot with sufficient clearance to permit it to move readily in a radial direction.
  • the blade is preferably flat and rectangular in planform and is slightly shorter than the axial distance between the end walls to provide clearance at each end of the blade.
  • the outer free edge of the blade is straight and smooth and adapted to contact the inner surface of the inertia ring in sealing engagement at all times during operation to define the initial point of a motor cavity of variable volume and peripheral extent between the core and the inertia ring and the end point of an exhaust cavity of variable volume and peripheral extent between the core and the inertia ring.
  • Inlet and outlet ports are provided in one end wall, and in the presently preferred embodiment are provided in both end walls.
  • the inlet port communicates with the work chamber on the motor side of the blade and the outlet port communicates with the work chamber on the exhaust side of the blade.
  • the inertia ring is of such radial thickness that its end face completely covers the inlet and outlet ports when the ring closely approaches the core in the zone of each respective port. When the ring is spaced the maximum distance from the core in the zone of each port, it partially uncovers the port for the passage of fluid.
  • the end face of the ring thus serves as the sole valving means for each of the ports and it successively opens and closes them at the proper time and to the proper extent during each cycle of its gyrations.
  • the inlet port is in communication with a source of compressed fluid by way of a fluid passage.
  • the size, shape, location and relative attitude of the inlet and outlet port are so chosen that there is always in the work chamber between the ring and the core a sufficient mass of pressurized fluid to transmit the centrifugal force of the ring to the core while maintaining them slightly separated at the zone of closest approach. Hence the ring does not roll on the core, thus preventing the wear which would otherwise occur. Actually the ring need not rotate about its own axis in operation because it is free floating and oscillatory in nature.
  • the condition of the pressure fluid is modified in its travel from the source to the inlet port.
  • flowing compressed fluid possesses both the kinetic or velocity energy resulting from its rate of flow and the potential expansion energy resulting from its compression. It has been found that the linear mass velocity of flow through a channel or passage is highly variable and to a great extent uncontrollable. On the other hand, the velocity of pure expansion is limited by a unique circumstance. At any constant temperature, if the back pressure or dumping area pressure is about one half the pressure of the compressed fluid or less, then the fluid will expand into the dumping area at a fixed velocity throughout a wide range of pressures, the velocity of expansion being related to the molecular, or atomic orbital velocity of the composition of the selected fluid.
  • FIGURE 1 is a sectional elevational view of the apparatus embodying the invention
  • FIGURE 2 is a sectional view taken on line 22 of FIGURE 1;
  • FIGURE 3 is an exploded view in perspective of the principal working parts of the apparatus
  • FIGURES 4 to 9 are schematic views illustrating the relation of parts at various stages in one cycle of operation
  • FIGURE 12 is a schematic view illustrating a modification of the inertia ring and barrier blade.
  • the spool-shaped supporting member comprises an axle member 10 having an enlarged centrally located cylindrical core 12 and reduced first and second ends 14 and 16, on which are mounted end walls or plates 18 and 20.
  • the end walls fit snugly on the axle ends and are held tightly in engagement with the core by the threaded members 22 and 24.
  • the flat, laterally extending inner faces 26 and 28 of members 18 and define with the surface of core 12 a cylindrical work chamber 30.
  • the inner diameter of the inertia ring is substantially larger than the diameter of the core to permit substantial movement of the ring in all directions radial of the core, and its length in an axial direction is slightly less than the longitudinal distance between the inner faces 26 and 28 of the end walls to provide adequate clearance.
  • the ring oscillates or gyrates about the core in an FIGURES 10 and 11 are similar views illustrating the r orbital path in response to force exerted by pressure fluid admitted to the work chamber. In a sense it can be said to swing about the core so that it is always eccentrically located with one portion of its inner surface 34 always quite close to the surface of the core but separated by a small gap 40 for reasons to be explained later.
  • a casing 42 having a closed end 44 snugly surrounds end walls 18 and 20 and completes the enclosure of the work chamber.
  • a second casing member 46 forms a continuation of casing 42 to enclose the entire apparatus.
  • Means to provide pressure fluid to the work chamber includes a fluid passage 48 extending longitudinally through the axle member and slightly displaced laterally from its axis.
  • the passage is divided into three sections.
  • the first and largest section 50 is at end 16 of the axle and receives pipe 52 which transmits compressed fluid from a source not shown.
  • the pipe is mounted Within the neck 54 of easing member 46 by means of a spider fitting 56 and is sealed to the axle by conventional O-rings 58.
  • the pressure fluid may be any suitable compressible fluid but preferably is air because of cheapness and availability. Air compressors are almost universally available at construction sites and usually provide air at pressures of 90 to 120 p.s.i.
  • section 50 is considerably larger than the passage in pipe 52 it serves as an expansion chamber which transforms much of the velocity energy of the mass flow into potential expansion energy.
  • Passage 60 in end wall 20 extends laterally from chamber 50 and then axially into inlet port 62 which opens into the work chamber 30. These two bends which change the direction of flow serve to further transform velocity energy into potential expanslon energy.
  • Central section 64 of passage 48 is considerably smaller than section 50 because approximately half of the total flow of fluid is diverted into passage 60.
  • End section 66 is smaller than section 64 to maintain a higher pressure in the latter for reasons to be mentioned later.
  • Section 66 discharges into expansion chamber 68 which serves in the same way as section 50 to change the direction of flow and transform velocity energy into potential expansion energy.
  • Inlet port 70 communicates directly with chamber 68 to admit pressure fluid into the work chamber. It is located directly opposite inlet port 62 and is of the same size and shape to provide balanced flow of pressure fluid.
  • a rectangular slot 72 is formed in core 12 and extends longitudinally for the length of the core and radially to its outer surface from a location near the core axis.
  • Barrier blade 74 is mounted in the slot and is in the form of a fiat rectangular plate slightly shorter than the distance between the end walls to provide clearances 76. Its outer free edge 78 is straight and smooth for sealing contact with the inner surface 34 of the inertia ring.
  • Auxiliary ports 80 and 82 are formed in end walls 1 8 and 20 in axial alignment with the blade to lead pressure fluid to clearances 76. The balanced pressure against the two ends of the blade centers it and keeps it clear of the end wall faces to minimize friction.
  • inlet ports 62 and 70 include slots having a generally arcuate form extending peripherally part way around the core.
  • Each port is on the motor side of the blade 74, originates adjacent thereto, and extends about sixty degrees. It is arranged eccentrically or spirally so that the end adjacent to the blade is closer to the core.
  • a plurality of passages 90 are arranged peripherally around the end wall and at least some of them are partially uncovered at all times so that the leakage fluid can discharge.
  • Outlet ports 92 and 94 are also elongate and generally arcuate or spiral. They extend peripherally around the core about one hundred eighty degrees with terminal ends adjacent to the blade 74 on the exhaust side and closer to the core than the originating ends. With the inertia ring and the blade in the positions shown in FIGURES 2 and 3 they combine with the core to form a motor cavity 96 to the left of the blade between the ring and the core and an exhaust cavity 98 between the ring and the core to the right of the blade. The orbital movement of the inertia ring is counterclockwise as viewed in these and subsequent figures. In FIGURE 2 it will be seen that both the inlet and outlet ports are partially uncovered or opened.
  • FIGURES 4 to 9 The sequence of steps which produce the gyratory motion of the inertia wheel are schematically illustrated in FIGURES 4 to 9, with the apparatus operating at full design load.
  • the arrangement of FIGURE 4 represents the zero degree position and the 360 degree position.
  • the inertia ring is in its uppermost position, being held out of contact with the core, as indicated at gap 40, by the fluid pressure as previously explained.
  • Blade 74 is in its uppermost position in sealing contact with the ring, and the motor cavity 96 and exhaust cavity 98 are exactly equal in size.
  • Inlet port 62 is open to its maximum extent, and the pressure fluid is entering and expanding to increase the size of the motor cavity.
  • Outlet port 92 is open slightly less than its maximum extent, allowing the fluid to exit so that the exhaust cavity can decrease in volume.
  • FIGURE 5 represents the 60 degree stage.
  • the inlet port is still wide open and the motor cavity has been enlarged.
  • the outlet port and the exhaust cavity have been decreased in size.
  • the inlet port begins to close, and it will be seen that at the 120 degree position of FIGURE 6 the inlet port is closed while the pressure remaining in the motor cavity causes the cavity to generate counterclockwise in accordance with a constantly increasing exhaust port which becomes static at FIGURE 9 as the inlet port begins to open.
  • the inlet port is still closed, and there is only one cavity, which is open to exhaust.
  • the motor cavity of the next cycle begins to form but the increase is small, and fluid entering through passage 88 from passage 64 is sufiicient to provide the motive power.
  • outlet port 92 is wide open.
  • the inlet port again begins to open and is partially open as shown in FIGURE 9 at 300 degrees.
  • the inlet port continues to enlarge until it is again wide open 6 at zero degrees in FIGURE 4.
  • the motor cavity is initiated at 180 degrees and increases through zero to a maximum at degrees when the outlet port again begins to open, turning it into an exhaust cavity.
  • inlet area begins to open.
  • inlet area is wide open.
  • inlet area is constant.
  • inlet area gradually closes.
  • inlet area is fully closed.
  • outlet area begins to open at the bottom.
  • outlet area is wide open.
  • outlet area is constant.
  • outlet area gradually closes.
  • outlet area at the top cavity is fully closed.
  • the inlet port admits suflicient fluid to provide the necessary power for the full design load while allowing the full useful expansion of the fluid down to a practical exhaust pressure, and the inlet is fully out 01f as the outlet port begins to open.
  • FIGS 7, 8 and 9 show the radially outwardly movement of the blade during which time the inlet port is closed or substantially closed, and the radially inwardly movement of the blade in FIG- URES 4, 5 and 6 during which time the inlet port opening into the chamber 30 degreases from a partial open condition to a closed condition.
  • the orbital velocity of the inertia ring can be maintained equal to or slightly greater than the velocity of such expansion and thus through the use of a predetermined configuration and positioning of the inlet and outlet ports, the end walls, and the valving of the ports by the orbiting of the inertia ring, it is possible to maintain the rate of fluid expansion equal to or slightly less than the orbital velocity of the inertia ring.
  • the volume of the fluid at any instant in time is substantially the same as the volume of the working chamber for the same instant of time and there is no instigation for volume increase of the working chamber which would result in the inertia ring contacting the exterior surface of the core 12.
  • FIGURE 4 it is easy to visualize the starting of the apparatus where the orbital position of the inertia ring is as depicted therein.
  • the position of the inertia ring may very well by chance be other than as shown in FIGURE 4, for instance see the position as shown in FIGURE 7.
  • the inlet ports are fully closed.
  • all of the fluid pressure is directed into the slot under the blade.
  • a suflicient force is generated against the blade causing it to lift the ring into the starting position as shown in FIGURE 4.
  • sufficient fluid flows through channel 88 and the slot 72 to cause an increase in the volume of the working chamber thereby initiating counterclockwise rotation of the inertia ring prior to the actual opening of the inlet ports.
  • the apparatus is designed to develop a constant external amplitude of motion over a wide range of external loads, producing maximum inertia ring eccentricity during maximum resistance and reduced eccentricity during reduced resistance.
  • the frequency of the cycle of operation is increased. This higher frequency reduces the expansion time available for the fluid during the angular generation of the motor cavity, and therefore the instantaneous fluid volume and consequently the cavity volume will be less at any given instant.
  • FIGURES 10 and 11 show the positions of the inertia ring at the zero and 180 degree stages. It will be noted that the gap 40 is considerably larger at the lower load.
  • the lesser eccentricity of the ring reduces the maximum opening of the inlet and outlet port-s, thus automatically reducing the quantity of fluid expended.
  • the eccentric or spiral arrangement of the inlet and outlet ports also automatically adjusts the timing of inlet and exhaust for maximum efliciency, and compatibility with the load situation within the load capacity of the apparatus.
  • the core 106 is basically similar to core 12 of FIGURE 1 and is provided with a similar slot 108.
  • Barrier blade 110 is slidably mounted therein, and its outer end fits into notch 112 in the inertia ring 114 in sealing relation. It is connected thereto for rocking motion by pivot pin 116 carried by the inertia ring. The motion and operation are just the same as in the embodiment previously described.
  • Apparatus for generating vibrations comprising: a fixed, spool-shaped supporting member having a central axially directed cylindrical core and laterally extending end walls defining a work chamber; an inertia ring surrounding said core Within said work chamber and having an inner diameter greater than the outer diameter of said core to permit oscillatory movement of said inertia ring in all directions radial of said core; a barrier blade extending longitudinally of said core and mounted therein for sliding movement radially thereof in sealing engagement with said ring and arranged to define the initial point of a motor cavity of a variable volume and peripheral extent between said core and said inertia ring and the end point of an exhaust cavity of variable volume and peripheral extent between said core and said inertia ring; a pressure fluid inlet port in an end wall communicating with said work chamber on the motor side of said blade; a pressure fluid outlet port in an end wall communicating with said work chamber on the exhaust side of said blade; said inlet port being in the form of an elongate arcuate slot
  • Apparatus for generating vibrations comprising: a fixed, spool-shaped supporting member having a central, axially directed cylindrical core and laterally extending end walls defining a work chamber; an inertia ring sur rounding said core within said work chamber and having an inner diameter greater than the outer diameter of said core to permit oscillatory movement of said inertia ring in all directions radial of said core; a barrier blade extending longitudinally of said core and mounted therein for sliding movement radially thereof in sealing engagement with said ring and arranged to define the initial point of a motor cavity of variable volume and peripheral extent between said core and said inertia ring and the end point of an exhaust cavity of variable volume and peripheral extent between said core and said inertia ring; a pressure fluid inlet port in an end wall communicating with said work chamber on the motor side of said blade; a pressure fluid outlet port in an end wall communicating with said work chamber on the exhaust side of said blade; means to supply pressure fluid to said inlet port; said inertia
  • Apparatus for generating vibrations comprising: a fixed, spool-shaped supporting member having a central, axially directed cylindrical core and laterally extending end walls defining a work chamber; an inertia ring surrounding said core within said work chamber and having an inner diameter greater than the outer diameter of said core to permit oscillatory movement of said inertia ring in all directions radial of said core; a barrier blade extending longitudinally of said core and mounted therein for sliding movement radially thereof in sealing engagement with said ring and arranged to define the initial point of a motor cavity of variable volume and peripheral extent between said core and said inertia ring and the end point of an exhaust cavity of variable volume and peripheral extent between said core and said inertia ring, the outer edge of said barrier blade being pivotally connected to the inner face of said inertia ring; a pressure fluid inlet port in an end wall communicating with said work chamber on the motor side of said blade; a pressure fluid outlet port in an end wall communicating with said work chamber on the
  • Apparatus for generating vibrations comprising: a fixed longitudinally extending axle member having a centrally located axially directed enlarged cylindrical core; a pair of end plates on said axle member extending laterally at the ends of said core to define therewith a cylindrical work chamber; an inertia ring surrounding said core within said work chamber and having an inner diameter greater than the outer diameter of said core to permit oscillatory movement of said inertia ring in all directions radially of said core; a casing surrounding all of said component and having a closed end defining a first expansion chamber at a first end of said axle member; said axle member having a longitudinal fluid passage therethrough communicating at said first end with said first expansion chamber; a conduit connected to a source of fluid pressure and with the fluid passage in the axle member at the second end of said axle member; a longitudinally and radially extending slot in said core; a barrier blade mounted in said slot for radial movement; the outer free edge of said blade being straight and smooth and adapted to contact the inner surface of said iner
  • said partition including a blade mounted in a longitudinally extending slot formed in the core for radial sliding movement therein;
  • a fluid inlet port and a fluid outlet port which are opened and closed cyclically in response to movement of the ring relative to the core to permit one of the cavities to be subjected to fluid pressure and the other to be exhausted;
  • auxiliary ports formed in said end walls for supplying fluid pressure to said clearances to prevent physical contact between the end walls and the end faces of the inertia ring and blade.
  • Apparatus for generating vibrations comprising: a fixed, spool-shaped supporting member having a central, axially directed, hollow, cylindrical core and laterally extending end walls defining a work chamber, said core having a longitudinally extending slot formed therein; an inertia ring surrounding said core within said work chamber and having an inner diameter greater than the outer diameter of said core to permit oscillatory movement of said inertia ring in all directions radial of said core; a barrier blade extending longitudinally of said core and mounted Within said slot for sliding movement radially thereof in sealing engagement with said ring and one of the surfaces of said slot to define the initial point of a motor cavity of variable volume and peripheral extent etween said core and said inertia ring and the end point of an exhaust cavity of variable volume and peripheral extent between said core and said inertia ring; means for supplying pressurized fluid through said slot into said motor-cavity; a pressure fluid inlet port in an end wall constructed to be disposed in intermittent communication with
  • said inlet port being in the form of an elongate arcuate slot, said arcuate slot being eccentric to said core, with the end of the slot adjacent to the barrier blade being closer to said core than is the opposite end of the slot.
  • outlet port being in the form of an elongate arcuate slot, said arcuate slot being eccentric to said core, with the end of the slot adjacent to the barrier blade being closer to said core than is the opposite end of the slot.
  • Apparatus for generating vibrations comprising:
  • a supporting member having a hollow core with a longitudinally extending slot formed in a wall portion thereof and end walls defining a work chamber;
  • an inertia ring surrounding said core within said work chamber and having an inner diameter greater than the outer diameter of said core to permit oscillatory movement of said inertia ring in all directions radial of said core;
  • a barrier blade mounted for sliding movement substantially radially within the slot of said core and being adapted to contact in sealing engagement the inner surface of said inertia ring and a surface portion of said slot at all times during operation to define the initial point of a motor cavity of variable volume and peripheral extent between said core and said inertia ring and the end point of an exhaust cavity of variable volume and peripheral extent between said core and said ring;
  • a pressure fluid outlet port in an end wall communicating with said exhaust cavity and having intermittent communication with said motor cavity;
  • said inertia ring being adapted to oscillate about said core in an orbital path with at least one of its end faces acting as a valve to cyclically and successively open and close said inlet and outlet ports;
  • means for moving said inertia ring orbitally relative to said core including means for supplying to said inlet port for introduction into said motor cavity, during at least approximately one-half of each cycle, a predetermined amount of fluid of substantially constant pressure and without substantially any linear mass velocity whereby the volume of fluid supplied to said motor cavity in combination with the increase in vol ume of fluid occurring from expansion of the fluid within said motor cavity equals, during pressurization of the motor cavity, the instantaneous volume of said motor cavity;
  • said outlet port when disposed in communication with said motor cavity, effecting at least a partial decompression of said motor cavity, and said outlet port, when disposed in communication with said exhaust port, effecting an exhaustion of said exhaust cavity.
  • Apparatus for generating vibrations in which a hollow cylindrical weight in the form of an inertia ring is movable in an orbital path about a centrally located cylindrical core within said ring having a diameter less than the inner diameter of the inertia ring, a work chamber thus being formed between the ring and the core;
  • a partition disposed within said slot means and dividing the work chamber into two cavities of variable volume, one of said cavities being a motor cavity and the other being an exhaust cavity, said partition being disposed in sealing engagement with said slot means and a surface of said ring;
  • said work chamber having a fluid inlet port in communication with said motor cavity and a fluid outlet port in intermittent communication with said motor cavity and said exhaust cavity; said ports being opened and closed cyclically in response to movement of the ring relative to the core to permit:
  • means for orbitally moving said inertia ring relative to said core during operation of the apparatus including means for supplying to said inlet port for introduction into said motor cavity, during at least approximately /2 of each cycle, a predetermined amount of fluid of substantially constant pressure and without substantially any linear velocity whereby the volume of fluid supplied to said motor cavity in combination with the increase in volume of fluid occurring from expansion of fluid within said motor cavity equals ,during pressurization of the motor cavity, the instantaneous volume of said motor cavity;
  • said outlet port effecting (i) at least a partial decompression of said motor cavity when disposed communication therewith;
  • the inlet port is an elongate arcuate slot formed in one end wall adjacent the path of orbital movement of the adjacent end face of the inertia ring such that the inlet port is subsantially covered by said end face during approximately one-half of each orbital cycle of the inertia ring.
  • An apparatus for generating vibrations comprising:
  • a barrier disposed Within said slot and in sealing engagement with both a surface of said slot and said inertia ring, said barrier blade cooperating, at any given time during operation of the apparatus, with said gap to divide the work chamber into:
  • a fluid inlet port in a wall of said work chamber and constructed to be disposed in intermittent communication with the motor cavity;
  • a fluid outlet port in a wall of said work chamber and constructed to be disposed in intermittent communication with the motor and exhaust cavities, said oscillatory movement of said inertia ring effecting opening and closing of said inlet and outlet ports;
  • said means for moving said inertia ring orbitally relative to said member including means for supplying to said inlet port for introduction into said motor cavity, during at least approximately one-half of each cycle, a predetermined amount of fluid of substantially constant pressure and without substantially any linear mass velocity whereby the volume of fluid supplied to said motor cavity in combination with the increase in volume of fluid occurring from expansion of the fluid within said motor cavity equals, during pressurization of the motor cavity, the instantaneous volume of said motor cavity;
  • An apparatus as described in claim 19 including means for moving said inertia ring radially during a predetermined portion of each cycle of said ring, said means including said barrier and means for supplying pressurized fluid against a surface portion of said barrier.
  • Apparatus for generating vibrations comprising: a fixed, spool-shaped supporting member having a central, axially directed, hollow, cylindrical core and laterally extending end wall defining a work chamber, said core having a longitudinally extending slot formed therein; an inertia ring surrounding said core within said work chamber and having an inner diameter greater than the outer diameter of said core to permit oscillatory movement of said inertia ring in all directions radial of said core; a barrier blade extending longitudinally of said core and mounted within said slot for sliding movement radially thereof in sealing engagement with said ring and one of the surfaces of said slot and arranged to define the initial point of a motor cavity of variable volume and peripheral extent between said core and said inertia ring and the end point of an exhaust cavity of variable volume and peripheral extent between said core and said inertia ring; a pressure fluid inlet port in each end wall communicating with said work chamber on the motor side of said blade; a pressure fluid outlet port on each end wall communicating with said work chamber
  • inertia ring having an axial length slightly less than the actual distance between said end Walls to provide a clearance between the ring and said end walls; said. inlet ports being of such size and location that the end faces of said inertia ring at least partially overlies same at all times; said inlet ports serving to supply pressure fluid to said clearances to prevent physical contact between the end walls and the end faces of said inertia ring.
  • the method of claim 24 including the steps of changing the direction of said fluid by about 90 at least two times between entry of said fluid into said conduit and introduction of said fluid into said motor cavity.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Hydraulic Motors (AREA)
  • Finish Polishing, Edge Sharpening, And Grinding By Specific Grinding Devices (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Reciprocating Pumps (AREA)
US559904A 1966-06-23 1966-06-23 Apparatus and method for generating vibrations Expired - Lifetime US3460808A (en)

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BE (1) BE700211A (enrdf_load_stackoverflow)
DE (1) DE1558829B2 (enrdf_load_stackoverflow)
GB (1) GB1187662A (enrdf_load_stackoverflow)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3650509A (en) * 1970-09-29 1972-03-21 Malan Vibrator Co Inc Free rotor vibrator
US3726508A (en) * 1970-12-22 1973-04-10 Inst Gornogo Dela Sibirskogo O Pneumatic vibrator
US3755972A (en) * 1970-05-14 1973-09-04 Nitto Kohki Co Portable sander
US3814385A (en) * 1972-01-13 1974-06-04 Vibro Verken Ab Regulator for pneumatic vibrator

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4330282A (en) * 1979-11-05 1982-05-18 Syntex (U.S.A.) Inc. Rotor driven vibratory device having rotor centralization means and vibrational mode selection means associated therewith
CN117740446B (zh) * 2024-02-20 2024-04-26 中国科学院东北地理与农业生态研究所 植物根际土壤采集装置

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2763472A (en) * 1954-01-07 1956-09-18 Fontaine Michel Rotary vibrator
FR1207855A (fr) * 1958-07-18 1960-02-19 Procedes Tech Const Perfectionnements aux appareils de serrage du béton par vibration
US3162426A (en) * 1961-06-23 1964-12-22 Vibratechniques Sa Vibrator

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2763472A (en) * 1954-01-07 1956-09-18 Fontaine Michel Rotary vibrator
FR1207855A (fr) * 1958-07-18 1960-02-19 Procedes Tech Const Perfectionnements aux appareils de serrage du béton par vibration
US3162426A (en) * 1961-06-23 1964-12-22 Vibratechniques Sa Vibrator

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3755972A (en) * 1970-05-14 1973-09-04 Nitto Kohki Co Portable sander
US3650509A (en) * 1970-09-29 1972-03-21 Malan Vibrator Co Inc Free rotor vibrator
US3726508A (en) * 1970-12-22 1973-04-10 Inst Gornogo Dela Sibirskogo O Pneumatic vibrator
US3814385A (en) * 1972-01-13 1974-06-04 Vibro Verken Ab Regulator for pneumatic vibrator

Also Published As

Publication number Publication date
GB1187662A (en) 1970-04-15
DE1558829A1 (de) 1970-04-23
BE700211A (enrdf_load_stackoverflow) 1967-12-20
DE1558829B2 (de) 1972-09-21

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