US3727890A - Vibrator for, and method of compacting concrete and similar masses - Google Patents

Vibrator for, and method of compacting concrete and similar masses Download PDF

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Publication number
US3727890A
US3727890A US00188905A US3727890DA US3727890A US 3727890 A US3727890 A US 3727890A US 00188905 A US00188905 A US 00188905A US 3727890D A US3727890D A US 3727890DA US 3727890 A US3727890 A US 3727890A
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Prior art keywords
mass
housing
control
vibrator
ball
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US00188905A
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English (en)
Inventor
F Seidl
P Uebel
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Wacker Werke GmbH and Co KG
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Wacker Werke GmbH and Co KG
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Priority claimed from DE19702050364 external-priority patent/DE2050364C3/de
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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
    • E—FIXED CONSTRUCTIONS
    • E04—BUILDING
    • E04G—SCAFFOLDING; FORMS; SHUTTERING; BUILDING IMPLEMENTS OR AIDS, OR THEIR USE; HANDLING BUILDING MATERIALS ON THE SITE; REPAIRING, BREAKING-UP OR OTHER WORK ON EXISTING BUILDINGS
    • E04G21/00—Preparing, conveying, or working-up building materials or building elements in situ; Other devices or measures for constructional work
    • E04G21/02—Conveying or working-up concrete or similar masses able to be heaped or cast
    • E04G21/06—Solidifying concrete, e.g. by application of vacuum before hardening
    • E04G21/08—Internal vibrators, e.g. needle vibrators

Definitions

  • the rate of supply of fluid to the v chamber is regulated by a control sensitive to the am- [301' Foreign Application nty Data plitude of movement of the eccentric mass so that 0m. 14, 1970 Germany ..1 20 50 364.4 when thevibrator is engaged with the material to be 1 compacted there is maximum fluid flow to the 52 useci. .;2s9/ 1 R, 259/1310. 43 ehember end when the vibrator is disengaged from the 51 Int Cl. ..B01f 11/00 material" Supply of fluid the chamber is [58 Field of Search .259/010. 42, DIG. 43,
  • PATENTEI APR 1 7 I975 SHEET 1 OF 3 PRESSURE MEDIUM FIG -2 PRESSURE MEEiIUM a a m w v 7 M V 7 w/ t 7 9L d M 8 IT/ /g x A, Z v w y P m 6 9 5 3 4 mm P PATENTEDAPR 1 11915 3.127. 890
  • the present invention relates to a vibrator for and method of compacting concrete or similar masses, according to which an eccentric mass is acted upon by a pressure medium, for instance, air, and rotated so as to roll in the housing of the vibrator.
  • a pressure medium for instance, air
  • the media to be compacted by means of the vibrator are compacted by supplying a constant quantity of pressure medium.
  • the speed of the eccentric mass increases considerably and reaches very high values because the supplied quantity of pressure medium is calculated in conformity with the quantity of pressure medium required for the speed when the vibrator works under load, and it will be appreciated that in order to obtain this speed, a relatively high quantity of pressure medium is necessary in view of the fact that the air resistance of the eccentric grows considerably when the vibrator works under load.
  • an object of the present invention to provide a vibrator for and method of compacting concrete, which will overcomethe above mentioned drawbacks and will permit the operator to concentrate his mind fully upon the compacting operation so that independently of the judgment of the operator, the ecology will be properly taken into consideration, which means that undue environmental noise development will be prevented, while on the other hand, the consumption of pressure medium will be reduced over that employed with heretofore known vibrators.
  • FIGS. 1 to 5 respectively illustrate five different embodiments of the present invention.
  • FIG. 6 is an enlargement of the central portion of FIG. 5.
  • the vibrator and method according to the present invention is characterized primarily in that the quantity of the pressure medium supplied to the eccentric mass for actuating the same is automatically so controlled that the speed of the eccentric mass during the idling of the vibrator will not materially exceed the speed calculated for the vibrator working under load.
  • the method according to the invention may be carried out in such a way that the quantity of the pressure medium is so controlled that the speed of the eccentric mass remains substantially constant when the vibrator works under load.
  • the quantity of pressure medium supplied to the eccentric mass adapts itself precisely to the compacting power required by the vibrator.
  • the control of the supply of pressure medium for the idling operation of the vibrator may be effected so that the idling speed of the eccentric mass remains either approximately at the value provided for the vibrator when working under load, or may even drop below this value, which is particularly advantageous with regard to ecology.
  • the method according to the invention may be practiced principally also by heretofore known vibrators.
  • it is merely necessary to measure the speed of the eccentric mass for instance, by electronic means, and to control the supply of pressure medium to the eccentric mass in conformity with the thus measured speed. This may easily be effected outside the vibrator.
  • it is considerably simpler and less expensive to practice the method according to the invention by providing the vibrator itself with means which will effect the control in conformity with the present invention.
  • a vibrator according to the present invention may be characterized in that the path on which the eccentric mass rolls in the housing of the vibrator is so designed that the circulating eccentric mass exerts a controlling or adjusting force upon a control element which in the vibrator housing is adjustable against a constant and stroke-dependent variable counter force preferably in the direction of the axis of rotation of the eccentric mass and controls the supply of the pressure medium to said eccentric mass.
  • the characteristics of the adjusting force and the counter force determine the speed behavior of the eccentric mass during the idling of the vibrator and when the vibrator works under load, and are to be selected in conformity with the requirement of the method of the invention.
  • eccentric masses preferably a ball may be used.
  • the rolling path of the eccentric mass is formed by a part fixedly connected to the vibrator housing and movable relative thereto under the pressure exerted by the eccentric mass onto its rolling path of track against the counter force, said movable part actuating a control element.
  • the movable part of the rolling path is preferably designed in a truncated cone-shaped manner.
  • the rolling path along which the eccentric mass rolls may be formed by a sleeve which is displaceable in the direction of the axis of rotation of the eccentric mass in the vibrator housing against the counter force. This sleeve is adapted to act as valve or sliding element for varying the cross section of the flow passage through which the pressure medium passes toward the eccentric mass.
  • the rolling path for the eccentric mass which acts counter to the counter force, may be tapered and may be arranged stationarily in the vibrator housing.
  • the eccentric mass is adapted to press against a piston acted upon by the oncoming pressure medium, while the control element is connected to the said piston.
  • the stationary rolling path is preferably conical.
  • a dropping of the idling speed below the value selected for the vibrator working under load or a drop in the range of values may with this embodiment be realized by having the conical rolling path for the eccentric mass comprise sections of different inclination or the piston acted upon by the pressure of the supplied pressure medium is designed as a differential piston which generates a counter force that changes suddenly and instantaneously with constant pressure supply in conformity with the displacement stroke of the eccentric.
  • the last mentioned two steps may, if desired, also be applied simultaneously.
  • the control mass is formed by the eccentric itself
  • the eccentric mass merely has to carry out the function of an oscillation generator in the vibrator housing as is customary with heretofore known inner vibrators, so that when designing the last mentioned vibrator according to the invention in connection with the rolling path without compromise, attention has to be paid only to what is important for the realization of an optimum oscillation generation, including a rolling of the eccentric at as low a rolling resistance as possible and as high a rolling path diameter as possible with a given vibrator outer diameter.
  • a structurally particularly simple, reliable and control -wise sensitive construction of a control element with a control mass separated from the eccentric mass consists in that the control body is so arranged in the vibrator that its distance from the axis of rotation of the eccentric masses is variable under the influence of mass forces occurring during the vibration.
  • the control body is, preferably, against the action of the mass forces decisive for change of its distance from the axis of rotation of the eccentric masses, held by means of a predetermined counter force in a rest position closer to said axis, from which rest position it jumps out when the mass forces exceed the counter force, and to which rest position it automatically returns when the mass forces drop below a certain value.
  • This jumping out of the control body from its rest position or position of detention and its return to said position are taken advantage of for the direct or indirect control of the effective cross section of the pressure medium supply passage leading to the eccentric mass.
  • the control body preferably directly controls the cross section of a pressure medium passage, the magnitude of which is decisive for the variable effective cross section of the pressure medium passage to the eccentric mass.
  • This pressure medium passage may be formed by the pressure medium supply passage to the eccentric mass itself, which would correspond to a direct control by the control body, however, also on indirect control of the last mentioned passage may be provided.
  • One end face is acted upon continuously by the preferably not yet controlled connecting pressure or a pressure derived therefrom of the pressure medium conveyed to the eccentric mass, whereas the other end face of the control piston is acted upon by variable counter forces which, with inherent displacement of the control piston, and in open position of the pressure medium passage controlled by the control body, has a different magnitude than in the closing position of said control piston.
  • the counter force acting upon the control piston is preferably formed by a spring load and by the pressure of the pressure medium in a pressure medium chamber arranged in front of the pertaining end face of the control piston. Said pressure medium chamber communicates through a narrow throttling area with the flowoff passage behind the eccentric mass.
  • control piston symmetrically with regard to the axis of rotation of the eccentric mass and movable in the vibrator housing in the direction of said mass while the pressure medium passage which interconnects the end faces of the control piston, may be so arranged that it extends centrally through said pressure medium passage.
  • control piston there should furthermore be provided a hollow chamber which receives the control mass in the form of a ball.
  • said control mass should be held in its rest position or position of detention under the pressure acting upon the on-flowing side of the control piston at the mouth which faces the hollow control piston chamber and pertains to the pressure medium passage of circular cross section, which pressure medium passage is controlled by said onflowing side of the control piston.
  • the rolling path for the eccentric mass in the interior of the vibrator housing is, for purposes of encountering a main air resistance, preferably so designed that said eccentric mass rolls on said rolling path under line contact.
  • an eccentric mass 2 rolls on a rolling path which is formed by two truncated cone-shaped path sections 4 and 5.
  • the path section 5 is provided on a sleeve 6 which is movably arranged in housing I.
  • Sleeve 6 has a control edge 9 and rests against a fixed portion of housing 1 by means of elastic elements, which, in the specific instance shown, are formed by dish springs 7
  • the movable control edge 9 cooperates with a control edge 11 of the vibrator which control edge 11 is either formed by or forms a part fixedly connected to the housing.
  • the supply of pressure medium is effected through a feed line 8 and a flow passage 10.
  • the pressure medium for instance, air, passes through the feed line 8 into the flow passage 10.
  • the stationary control edge 11 and the movable control edge 9 located opposite said stationary control edge 11 and arranged on the displaceable sleeve 6
  • the pressure medium passes between the two control edges 9 and 11 and tangentially acts upon the eccentric mass 2 which rolls between the rolling path sections 4 and 5 forming the rolling surfaces to be engaged by the eccentric mass 2.
  • the eccentric mass In view of the fact that the eccentric mass is acted upon by the pressure medium, it rotates in the housing at a certain speed of rotation. The higher the speed of the eccentric mass 2, the greater will bethe generated centrifugal force, and the greater will also be the pressing force exerted upon the rolling path section 5.
  • the resistance of the eccentric mass 2 encountered on the rolling path 4, 5 depends on the degree to which the medium for instance, concrete, which is in contact with the vibrator housing 1, is compacted.
  • the running resistance is low when the vibrator is located outside of the medium to be compacted, and the running resistance increases considerably when the vibrator engages the medium to be compacted for instance, is immersed therein, in which instance the eccentric mass has the tendency to reduce its speed.
  • the rolling path section 5 is pressed away from the rolling path section 4 by the eccentric mass 2., In this way, the control edge 9 is moved toward the control edge 11 so that the cross section of the flow passage 10 will be narrowed. In view of the narrowing of the cross section, less pressure medium can flow through to act upon the eccentric mass 2.
  • the control strokes and control forces are so selected that the frequency of the eccentric mass remains constant.
  • a truncated coneshaped stationary rolling path 4 for the eccentric mass 2' in the vibrator housing 1, there is provided a truncated coneshaped stationary rolling path 4 for the eccentric mass 2'.
  • the inclination of the rolling path 4 brings about that the ball 2' which forms the eccentric mass will exert an adjusting force which, when viewing FIG. 2, is directed toward the upper side and which is exerted upon a piston 20 centrally adjustably located in the vibrator.
  • This piston 20 forms on that side thereof which faces away from the ball 2 a valve body 21.
  • Valve body 21 cooperates with a stationary valve seat 22 through which the pressure medium flows to the ball 2. From the control valve comprising the valve body 21 and the valve seat 22, the pressure medium passes through flow passages 23 and'24 to ball 2' and tangentially acts upon said ball 2' and rotates the same.
  • valve body 21 and piston 20 are continuously exposed to the pressure of the oncoming pressure medium, which pressure medium has the tendency to displace said body 21 and piston 20 in the direction toward the ball.
  • the piston 20 exerts upon the ball 2' a counter force acting counter to the upwardly directed adjusting force.
  • the degree of the throttling of the pressure medium flow at the valve 211, 22 represents a factor which is dependent on the speed of the ball.
  • the parts which are decisive for the generation of the adjusting force and the counter force are so dimensioned that the speed of the ball 2' in idling condition of the vibrator and under the load of the vibrator are, by a corresponding control of the pressure medium supply in the valve 21, 22, approximately constant.
  • FIG. 3 differs from that of FIG. 2 primarily in that the stationary rolling path 4" has two sections 4a" and 4b of a different inclination.
  • the right-hand section 4b which is closer to the valve 21, 22, has the greater inclination.
  • the speed starting from the above described low value, first drops further whereby the piston 20 will be able to push back the ball into the section 40" while simultaneously valve 21, 22 opens so that thereupon the speed of rotation of the ball due to the increased supply of pressure medium again increases to the higher value provided for the vibrator working under load.
  • the speed of rotation of the ball is held approximately constant at this higher value by the alternate action between the adjusting force of ball 2 and the counter force of piston 20 and the inherent control of the pressure medium supply.
  • FIG. 4 shows still another embodiment of the invention according to which the control element serving for producing the counter force also serves for controlling the pressure medium supply to the eccentric mass-balls 2 or 2' for a vibrator according to FIG. 2 or FIG. 3.
  • FIG. 4 is provided with a differential piston which has its right end face (with regard to FIG. 4) acted upon by pressure of the oncoming pressure medium and as a control piston controls the flow of the pressure medium into a flow passage 24 from which the pressure medium in a non-illustrated manner passes to the ball 2 or 2' which are tangentially acted upon by the pressure medium and are thus rotated.
  • a by-pass passage 25 is so provided that the pressure medium chambers on the upper side of the differential piston and of the oppositely located lower end face,which has a smaller effective cross section are in communication with each other when the flow control cross section controlled by piston 20'to the flow passage 24 is small, and that this connection is interrupted when the differential piston 20' in a further lower position frees a greater cross section.
  • the counter force generated by the differential piston 20' and conveyed by piston rod 26 upon the ball 2 or 2' has a low value which after closing the connection 25 changes instantaneously to a higher value.
  • a narrow throttling passage 27 prevents that, following the closing of the connection 25, the pressure medium on the left-hand side of differential piston 20 will form a pressure cushion which would affect the control movement of the differential piston 20'.
  • this vibrator has a housing mantle 28,which at the ends is closed by a head 29 and a connecting member 30 for the outer mantle 31 of a coaxial hose for supplying or withdrawing air.
  • Compressed air is conveyed to the vibrator through the inner hose 32 of the coaxial hose.
  • the air leaves the vibrator through the annular chamber between the inner hose 32 and the outer mantle 31 of the coaxial hose as is indicated by the arrows 33 and 34.
  • Into the housing mantle 28 of circular cross section there has been worked a rolling path 35 for the eccentric mass 36.
  • This rolling path is curved in conformity with the curvature of the ball 36 so that the latter will roll on said rolling path while contacting the same along a line.
  • the ball receiving chamber 37 is laterally confined by mantle inserts 38 and 39 which are somewhat spaced from the eccentric mass-ball 36 so that said ball will during its rolling action on track or path 35 not drag on said inserts 38, 39.
  • the inserts 38 and 39 always hold the eccentric mass-ball 36 in the vicinity of the rolling path 35 so that the ball will immediately center on said rolling path when it is acted upon by compressed air.
  • the compressed air is conveyed to the eccentric mass-ball 36 through a central bore 40 in the insert 39,
  • a radial passage 41 extends through the insert 39 up to the housing mantle 28, and a longitudinal passage 42 into which leads the radial passage 41.
  • the end member 43 of passage 42 which end member is adjacent to the ball 36, leads substantially tangentially with regard to the rolling path 35 into the ball receiving chamber 37 in order to convey an air flow to the eccentric mass-ball 36 which air flow hits the eccentric massball 36 substantially tangentially with regard to the circulatory path of said ball.
  • a sliding piston or valve spool 44 which in the position shown in the drawing engages a bore insert 45 that prevents the movement of said valve spool or control piston 44 downwardly t0 the eccentric mass ball 36, said bore insert 45 being fixedly located in bore 40.
  • That end of the bore insert 45 which faces toward the eccentric massball 36 is stepped or offset at its diameter so that between the wall of the bore 40 and the bore insert 45 there is provided an annular passage 46 from which branches off a radial passage 47 that leads into an axial passage 48.
  • This passage 48 is worked into the insert 39 located opposite passage 42 and leads into the annular chamber 49 between the housing mantle 28 and the inner hose 32.
  • the inner hose 32 is in open communication with the annular chamber between the inner hose 32 and the outer mantle 31 of the coaxial hose.
  • the compressed air which acts upon the eccentric mass-ball 36 out of the passage 43 can thus escape to the coaxial hose from the ball receiving chamber 37 through the passages 46, 47 and 48.
  • the sliding piston or valve spool 44 has hollow chamber 53 which is open to that portion of bore 40 which receives the fluid. From hollow chamber 53, a central axially directed bore 51 leads to the lower end face of the valve spool 44 which in this way connects the end faces thereof but in FIG. 5 position of valve spool 44 is closed by a control mass 52.
  • the control mass 52 is in the form of a ball which under the onflow pressure from the inner hose 32 in a rest or detained position, is located in the circular mouth of bore 51 in hollow chamber 53.
  • valve spool 44 On that side of the valve spool 44 which is adjacent to the bore insert 45, there is provided a hollow chamber 55 which is open toward the valve spool 44. Between the bottom of chamber 55 and the lower end face of valve spool 44, there is provided a spring 54 resting thereon. Spring 54 continuously urges valve spool 44 to move upwardly against the pressure acting from the inner hose 32 onto the upper end face of said valve spool 44.
  • a passage 56 behind the upwardly moving lower end face of valve spool 44 is freed.
  • This passage 56 establishes communication of the bore 40 with the axial passage 42 but has a narrower cross section than the passage 41.
  • a control mass-ball 52 with the here described control operation and control condition does not occupy its rest or retained position so that the bore 51 is open, it will be appreciated that now compressed air can pass from the inner hose 32 through bore 51 and throttling passage 55 into the axial passage 42 and from there to the eccentric mass-ball 36.
  • the quantity of the compressed air flowing onto the ball 36 is considerably less than before when the passage 41 was open.
  • the inner vibrator of FIG. operates as follows:
  • control mass-ball 36 oscillates with this amplitude while the arrangement is such that the ball 36 is at this oscillation amplitude safely held in its resting seat by the connecting pressure acting thereupon from the inner hose 32.
  • the mass forces acting upon the oscillation amplitude thus do not suffice to overcome the retaining or resting force.
  • the inner vibrator When after completion of the compacting operation, the inner vibrator is pulled out of the compacted medium, it undergoes a relief with inherent decrease in the running resistance for the eccentric mass-ball 36 and also has its oscillation amplitude increased.
  • the valve spool 44 blocks in the above described manner the passage 41 and simultaneously frees the passage 56 through which fluid pressure then acts upon the eccentric mass-ball 36 at a considerably less pressure than previously through passage 4i.
  • the speed of the ball 36 drops, but in view of the freeing of the inner vibrator,-
  • the essential advantage of the method and the vibrator according to the present invention consists in that the operator no longer has to devote his attention to the speed of the eccentric mass and no longer has manually to control the supply of pressure medium in order on one hand to prevent the speed of the eccentric mass from reaching undesired high values during idling operation.
  • the proper speed of the eccentric mass is assured during the compacting operation, and the automatic control of the speed of the eccentric mass reliably saves considerable quantities of pressure medium during the working intervals between the compacting operations.
  • a minimum of pressure medium is used, and only when the vibrator is placed under load will the consumption of the pressure medium rise to the value necessary for the compacting operation.
  • the speed of the eccentric mass will also during idling operation safely be relatively low so that the occurring surface pressure will remain below admissible limits. This in turn results in a long life of the parts of the vibrator.
  • the low speed during idling operation also maintains the noise development in tolerable limits so that the surrounding is protected against influences which may be harmful. Low speeds are important with regard to noise development particularly during idling because the vibrator when under load is in contact with the medium to be compacted which in its turn has a necessary damping effect.
  • the method of compacting material such as concrete, and the like, which comprises: providing an element for engagement with the material to be compacted, engaging the element by a mass movable in a variable diameter rotary path by fluid pressure and which will develop an eccentric load on the element and vibrate the element when the mass is actuated, supplying fluid under pressure to the mass to actuate the mass in the rotary path of movement thereof, and controlling the said supply of fluid to the mass in conformity with changes in the amplitude of the path of said mass.
  • a vibrator for compacting materials such as concrete and the like: a housing, an eccentric mass in the housing, a chamber in the housing larger than said mass in which the mass is located and in which the mass is moveable in a circular path to develop an eccentric load on said housing to cause vibration thereof, said housing at one end being engageable with the material to be compacted to impart said vibration thereto, a passage in said housing leading to said chamber and discharging substantially tangentially into said chamber for the supply of fluid under pressure to said mass to actuate said mass to move in said circular path, an exhaust conduit leading from said chamber, control means in said passage for controlling the rate of fluid flow therein, and means responsive to variations in the amplitude of movement of said mass in said chamber for adjusting said control means to control the supply of fluid to said mass.
  • a vibrator according to claim 6 in which said chamber in which the ball moves in a circular path comprises: a first axial stationary portion fixed in said housing on one side of the ball, and a second axial portion in the housing on the other side of the ball and axially moveable in the housing, means urging said second portion toward the ball, said second portion being operable when moved axially in the housing by the ball to actuate said control means.
  • a vibrator according to claim 7 in which said moveable second portion is cone shaped with the larger diameter end portion facing the said first stationary portion.
  • a vibrator in which said control means includes a sleeve in the housing movable axially therein, said sleeve being fixed to said second moveable portion so as to move therewith, said sleeve and said housing cooperatively forming a valve in said passage which varies in conformity with movement of said sleeve in said housing.
  • a vibrator according to claim 5 in which said chamber comprises opposed axial portions on opposite sides of said ball each tapering outwardly toward the ball and a peripheral portion extending axially between said axial portions and tapering outwardly in a direction toward said control means.
  • a vibrator according to claim 10 in which said control means comprises a valve piston having one end adjacent the path of said mass, the other end of said valve piston controlling said passage.
  • valve piston has opposed areas of different size therein, the larger of said areas being exposed to the incoming fluid supply, the smaller of said areas being connected to receive fluid from said supply and having restricted communication with said passage downstream from said control means.
  • control means includes a control mass separate from said eccentric mass and moveable for controlling the rate of fluid supply to said eccentric mass.
  • a vibrator according to claim 15 in which said control mass has a normal position on the axis of said housing and is displaceable radially therefrom under the influence of vibration of said housing.
  • a vibrator in which said control mass is normally in a radially centered position in said housing and is held therein by the pressure of the fluid in said passage, said control mass being moveable radially away from said position in response to a predetermined amplitude of vibration of said housing, said control mass when in said predetermined radial position permitting maximum rate of fluid flow to said chamber and when displaced radially from said position causing the rate of fluid flow to said chamber to reduce, said control mass returning to said radially centercd position in said housing in response to reduction in the amplitude of vibration of said housing.
  • a vibrator according to 'claim 17 which includes an unrestricted channel leading from said passage to said chamber and a restricted channel leading from said passage to said chamber, a valve member having first and second positions, a respective channel being open and the other closed in each position of said valve member, and means for actuating said valve member in response to movement of said control mass out of and into the said radially centered position thereof.
  • a vibrator according to claim 19 in which said valve member has opposite ends of equal area, one said said control mass is in centered position and opens said restricted channel when said control mass is displaced radially from said centered position.
  • a vibrator according to claim 20 in which said valve member is on the axis of said housing and is moveable axially in said housing, said conduit in said valve member being on the central axis thereof, said valve member having a recess on the said one end receiving said control mass, said control mass being a ball, and the bottom of said recess being conical.
  • a vibrator according to claim 15 in which said chamber comprises a peripheral wall formed on the inside of said housing andfo'rming the path for said eccentric mass, said eccentric mass rollingly engaging said path.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Architecture (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)
  • Road Paving Machines (AREA)
  • On-Site Construction Work That Accompanies The Preparation And Application Of Concrete (AREA)
  • Air-Flow Control Members (AREA)
US00188905A 1970-10-14 1971-10-13 Vibrator for, and method of compacting concrete and similar masses Expired - Lifetime US3727890A (en)

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DE19702050364 DE2050364C3 (de) 1970-10-14 Vibrator zum Verdichten von Beton oder ähnlichen Medien

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Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3814385A (en) * 1972-01-13 1974-06-04 Vibro Verken Ab Regulator for pneumatic vibrator
US3908965A (en) * 1972-07-06 1975-09-30 Wacker Werke Kg Compressed air operable inner vibrator for compacting concrete and the like
US4526049A (en) * 1981-02-26 1985-07-02 Jean Netter Vibrator
US4682896A (en) * 1985-03-04 1987-07-28 Esref Halilovic Device for generating vibrations
US4818115A (en) * 1984-10-02 1989-04-04 Toernqvist Peter J T Device to mechanically break apart a barrier
US5439290A (en) * 1992-06-05 1995-08-08 Shell Oil Company Fluid flow conduit vibrator and method
US5997172A (en) * 1997-05-15 1999-12-07 Micron Co., Ltd. Air-driven vibrator
US6213681B1 (en) * 1997-07-23 2001-04-10 Wacker-Werke Gmbh & Co., Kg Soil compacting device with adjustable vibration properties

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Publication number Priority date Publication date Assignee Title
CN107447987A (zh) * 2017-07-28 2017-12-08 贵州省水利水电勘测设计研究院 一种抽气式振捣棒
CN120139098B (zh) * 2025-05-16 2025-07-15 山西路桥建设集团有限公司 一种用于桥梁现浇湿接缝模板的悬吊设备以及悬吊方法

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2520044A (en) * 1949-10-21 1950-08-22 Donald E Mason Vibrating device

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2520044A (en) * 1949-10-21 1950-08-22 Donald E Mason Vibrating device

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3814385A (en) * 1972-01-13 1974-06-04 Vibro Verken Ab Regulator for pneumatic vibrator
US3908965A (en) * 1972-07-06 1975-09-30 Wacker Werke Kg Compressed air operable inner vibrator for compacting concrete and the like
US4526049A (en) * 1981-02-26 1985-07-02 Jean Netter Vibrator
US4818115A (en) * 1984-10-02 1989-04-04 Toernqvist Peter J T Device to mechanically break apart a barrier
US4682896A (en) * 1985-03-04 1987-07-28 Esref Halilovic Device for generating vibrations
US5439290A (en) * 1992-06-05 1995-08-08 Shell Oil Company Fluid flow conduit vibrator and method
US5997172A (en) * 1997-05-15 1999-12-07 Micron Co., Ltd. Air-driven vibrator
CN1096840C (zh) * 1997-05-15 2002-12-25 株式会社米库龙 气动式振动器
US6213681B1 (en) * 1997-07-23 2001-04-10 Wacker-Werke Gmbh & Co., Kg Soil compacting device with adjustable vibration properties

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GB1336031A (en) 1973-11-07
SE370642B (enrdf_load_html_response) 1974-10-28
JPS5243335B1 (enrdf_load_html_response) 1977-10-29
DE2050364A1 (de) 1972-06-29
DE2050364B2 (de) 1973-08-09
CH543659A (de) 1973-10-31
FR2109993A5 (enrdf_load_html_response) 1972-05-26

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