US3726508A - Pneumatic vibrator - Google Patents

Pneumatic vibrator Download PDF

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Publication number
US3726508A
US3726508A US00172421A US3726508DA US3726508A US 3726508 A US3726508 A US 3726508A US 00172421 A US00172421 A US 00172421A US 3726508D A US3726508D A US 3726508DA US 3726508 A US3726508 A US 3726508A
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United States
Prior art keywords
housing
impact
members
impact member
vibrator
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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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US00172421A
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English (en)
Inventor
E Varnello
N Klushin
P Maslakov
V Shmigalsky
E Abramenkov
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Institut Gornogo dela Sibirskogo Otdelenia Akademii Nauk SSSR
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Institut Gornogo dela Sibirskogo Otdelenia Akademii Nauk SSSR
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Priority claimed from SU1602014A external-priority patent/SU324789A1/ru
Application filed by Institut Gornogo dela Sibirskogo Otdelenia Akademii Nauk SSSR filed Critical Institut Gornogo dela Sibirskogo Otdelenia Akademii Nauk SSSR
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    • 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
    • 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
    • B06B1/183—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency wherein the vibrator is actuated by pressure fluid operating with reciprocating masses

Definitions

  • the present invention relates to construction machinery, and, more particularly, to submersible pneumatic vibrators for compacting concrete mixes.
  • a pneumatic vibrator which comprises a housing in the form of a closed cylinder having an impact member mounted for reciprocations therein under the action of compressed air and another member for imparting additional transverse vibrations to the housing, in the form of a cylinder with an eccentric projection facing the impact member and adapted to be engaged by the latter, with the bearing surface of this another member being spherical.
  • the last-mentioned member is freely mounted on the bottom, or terminal wall of the housing, with an annular clearance being left between the member and the cylindrical wall of the housing.
  • the vibrator also includes an air distributor which is either a valve or a slide valve cooperating with a system of passages and openings in the wall of the housing for alternate supply of compressed air into the working spaces and outlet of the used-up air into the atmosphere.
  • the air distributing means may have no valve means.
  • the part of the valve means is played by the impact member itself, there being provided axial and radial passages in the body of the impact member and annular grooves in the surface thereof.
  • the passages and the grooves alternatingly connect the working spaces within the housing with the above-mentioned passages and openings in the wall of the housing.
  • this known type of vibrators features a relatively low frequency of the additional transverse vibrations and does not provide for the circular character of these vibrations. Moreover, the transverse vibrations of this vibrator are of a small amplitude and of a simple shape, and the very low frequency component of these vibrations is practically absent.
  • a pneumatic vibrator comprising a housing defined by a cylinder with the closed ends, an impact member mounted for reciprocations therein, said impact member having passages and annular grooves in the body and in the peripheral surface thereof respectively for the passage of compressed air; a member for imparting additional transverse vibrations to said housing,
  • said vibrator comprises two impact-receiving members mounted in said housing with radial and axial clearances, adjacent to said end walls of said housing and connected therewith, said impact-receiving members being adapted to impart additional transverse vibrations to said housing, and said striking means being defined by eccentric projections on the respective opposite end faces of said impact member, adapted to engage said impact-receiving members at the impacts of said impact member.
  • said impact-receiving members for imparting additional transverse vibrations to said housing to be constituted by discs coaxial with the respective end walls of said housing, with said discs being resiliently connected with said end walls.
  • a protective cylinder is mounted interiorly of with said housing, said cylinder reciprocably receiving said impact member therein, and resilient means being said housing, as well as for said end walls to have coni-- cally tapering peripheral surfaces along which said members and said end walls will engage one another at the impacts of the impact member.
  • These impact-receiving members may be connected with said end walls by spherical bearing means.
  • transverse partition into chambers, to reciprocably one impact receiving member in each chamber with, said transverse partition serving in this case as an intermediate end wall of said housing, on which, similar to the aforesaid upper and lower end walls, is mounted discs cooperating with said impact members, for imparting additional transverse vibrations to said housing.
  • FIG. 1 shows schematically mainly in cross section a pneumatic vibrator embodying the invention, with the compressed air conducts disposed on the housing and the impact member being in its lowermost position;
  • FIG. 2 is a view taken along line II-II of FIG. 1;
  • FIG. 3 is a view taken along line III-III of FIG. 1;
  • FIG. 4 is a view taken along line IV-IV of FIG. 1;
  • FIG. 5 shows schematically the upper portion of the vibrator, illustrating the manner in which the housing of the vibrator is imparted additional transverse vibrations
  • FIG. 6 is a view taken along line VI-VI of FIG. 5;
  • FIG. 7 shows schematically mainly in cross section a pneumatic vibrator embodying the present invention, with the compressed air conduit disposed in the housing and the impact member in the topmost position;
  • FIG. 8 shows schematically the lower portion of the vibrator, illustrating the manner in which the-housing mount of the vibrator is imparted additional transverse vibrations
  • FIG. 9 is a view taken along line V-V of FIG. 8, illustrating the manner in which rotation of the impact member about its axis is effected;
  • FIG. 10 is a cross-sectional view of the impact member with the radially displaced gravity center
  • FIG. 11 shows schematically a longitudinally sectional view of pneumatic vibrator embodying the invention, incorporating a hollow shaft having built therein a profiled longitudinal partition;
  • FIG. 12 is a view taken along line VII-VII of FIG.
  • FIG. 13 is a view taken along line VIII-VIII of FIG. 1 1;
  • FIG. 14 shows the lower part of the vibrator having the impact member incorporating a one-way valve
  • FIG. 15 shows the open position of the one-way valve a partly broken-away view of FIG. 14;
  • FIG. 16 shows the lower portion of the vibrator incorporating a protective cylinder and a resilient interposing member
  • FIG. 17 is a view taken along line EE of FIG. 16;
  • FIG. 18 shows the lower portion of the vibrator incorporating the protective cylinder
  • FIG. 19 shows a pneumatic vibrator embodying the invention, having two impact members mounted in the housing thereof;
  • FIG. 20 shows the lower portion of the vibrator wherein the discs cooperate with the bottom walls of the housing
  • FIG. 21 shows the lower portion of the vibrator wherein the discs are connected with the bottom walls through spherical bearing means.
  • the pneumatic vibrator illustrated in FIGS. 1 to 7 includes a cylindrical closed housing 1 (FIGS. 1 and 7) within which there is mounted for reciprocation and rotation an impact member 2.
  • the body of the impact member 2 has made therein axial passages 3 and 4, radial passages 5 and 6, tangential passages 7 and 8 (FIGS. 3 and 4) and annular grooves 9, 10, 11 and 12, with the aforementioned passages and grooves serving to supply compressed air into working spaces 13 and 14 of the vibrator and to direct the used-up air therefrom into ambient atmosphere.
  • Outlets l5 and 16 of the tan-' gential passages 8 and 7, respectively, are disposed within the annular grooves 11 and 12.
  • the respective opposite end faces of the impact member 2 are provided with off-center projections 17 and 18, with their eccentricity relative to the axis of the impact member being equal to a (FIGS. 5 8), the projections serving to strike respective discs 19 and 20 (FIGS. 1 and 7), mounted within the housing 1 of the vibrator, at reciprocations of the impact member 2 and thus to impart additional transverse vibrations to the wall of the housing 1.
  • the discs 19 and 20 are mounted on the respective end walls 21 and 22 of the housing 1 with the help of resilient suspension members 23 and 24 which may be, for example, of rubber.
  • the impact member 2 acts itself as the air distributing means affecting the supply of compressed air alternatingly into the working spaces 13 and 14 inside the housing 1.
  • the compressed air is supplied into and the used-up air is exhausted from the vibrator through respective hoses 30 and 31 of rubber or any other suitable material.
  • the vibrator illustrated in FIGS. 1 to 8 operates, as follows.
  • Compressed air from a supply source flows through the air supply hose 30 into the air supply passage 25, from which it flows through the opening 27, the annular groove 9, the radial passage 5, the axial passage 3, the tangential passage 7, and the annular groove 11 into the working space 13 within the housing 1 (the direction of the air flow is indicated by arrow lines in the drawings).
  • the impact member is driven longitudinally toward the disc l9 (the upper disc in the appended drawings).
  • the impact member 2 is bodily rotated by the action of the reactive torque M (the direction of this torque is shown with the respective arrow line in FIG. 6).
  • the torque M can be found from the following equation:
  • l is the arm of the application of the reactive force R.
  • the impact member 2 strikes by its off-center projection 17 on the respective face end, upon the disc 19 at a point radially remote from the central axis of this disc, with the impact force being equal to P.
  • the housing 1 is imparted longitudinal vibrations, and as the disc 19 strikes against the internal wall of the housing 1, the latter is imparted additional transverse vibrations which are even more useful for the cause of deep compacting of concrete mixes, than the longitudinal vibrations.
  • the longitudinal vibrations help the vibrator to submerge rapidly into the concrete mix to be compacted, but the amplitude of these vibrations should not be excessively great.
  • the amplitude of the additional transverse vibrations of the housing 1 is directly proportional to the impact force P which, in turn, is directly proportional to the impact force P with which the impact member 2 strikes against the disc 19.
  • the amplitude of Iongitudinal vibrations is reduced on account of the resilient suspension members 23 and 24 having been provided intermediate of the end walls 21 and 22 of the housing 1 and the discs 19 and 20, respectively.
  • These resilient suspension members serve not only to reduce the amplitude of the longitudinal vibrations of the housing, but also to return the discs 19 and 20 into their initial normal position after their impacts with the impact member 2.
  • the working space 13 becomes connected in the fluid communication sense with the exhaust openings 29 and 28 in the wall of the housing 1, with the opening 28 communicating with the space 13 through the annular groove 11, the passages 7, 3 and 5, and the annular groove 9 in the body of the impact member 2. From these two exhaust openings, the used-up air flows through the discharge passage 26 and the discharge hose 31 into ambient atmosphere.
  • the annular groove 10 of the impact member 2 starts communicating with the opening 27 in the wall of the housing 1 (FIG. 7), whereby compressed air starts flowing from the passage 25 in the wall of the housing 1 through this annular groove 10, the radial passage 6, the axial passage 4, the tangential passage 8 (FIG. 6) and the annular groove 12 into the upper working space 14.
  • the action of the pressure of the compressed air within the space 14 upon the respective face end of the impact member 2 drives the latter for the return stroke toward the disc 20 (FIGS. 7 and 1).
  • the off-center projection 18 on the face end of the impact member 2 facing the disc 20, strikes the disc 20 at the point thereof, remote from the longitudinal axis, with the force P.
  • the rotation of the impact member 2 is brought about by the action of the reactive torque M, (FIG. 9) which can be found from the equation (1) hereinabove.
  • the disc 20 being mounted within the housing 1 with the radial clearance c and the axial clearance Q from the respective internal walls of the housing 1, as it has been already mentioned, and being connected to the wall 22 of the housing 1 through the resilient suspension member 24, the impact of the impact member 2 upon the disc 20 makes the latter deflect from its normal position and strike by its side cylindrical wall the internal cylindrical wall of the housing 1 with the force P (FIG. 8) creating the torque equal to
  • the torque M is responsible for the housing 1 being imparted an additional transverse vibration and a longitudinal vibration.
  • the working space 14 communicates with the exhaust openings 28 and 29, the opening 29 communicating now with the working space 14 through the annular groove 12, the passages 8, 4 and 6, and the annular groove in the body of the impact member 2. From the openings 28 and 29, the used-up air flows through the passage 26 in the wall of the housing 1 into the exhaust hose 31 and then into ambient atmosphere.
  • the annular groove 9 communicates with the supply opening 27 in the wall of the housing 1, and the above-described complete cycle of the operation of the vibrator is repeated.
  • the impact member 2 reciprocates in the housing 1 and also rotates therein. Therefore, the points of the successive impacts of the impact member 2 upon the discs 19 and 20 will be distributed along corresponding circles on the respective face ends of these discs. Consequently, the housing 1 of the vibrator is further imparted additional circular vibrations of a high frequency and with a certain amplitude, which fact also improves the quality'of the compacting of concrete mixes, performed by the vibrator.
  • the effectiveness of the compacting of concrete mixes can be further stepped up by a vibrator featuring variable parameters of its vibration (the amplitude, the frequency of vibrations, the agitating force).
  • the center of the gravity of the impact member should be displaced radially from the axis of the rotation thereof, i.e., from the point 0 into the point 0 (FIG. 10).
  • the displacement of the gravity center of the impact member through a distance b can be achieved by providing in the body of impact member 32 a hollow cavity 33.
  • the housing 1 is imparted further additional transverse vibrations, besides the transverse vibrations which the housing! is imparted by the impacts of the impact member 32 upon the discs 19 and 20 and by the impacts of these discs upon the housing 1.
  • the total agitating force will be then a variable value equal to the sum total of the agitating forces P and F.
  • the amplitude of the transverse vibrations created by the agitating force P can be increased, and the weight of the vibrator reduced by mounting within housing 34 (FIGS. ll, 12 and 13) a hollow shaft 35 having built therein a profiled partition 36 defining with the internal wall of the shaft 35 an air supply passage 37 and an air exhaust passage 38 which, in this modification of the herein disclosed vibrator, take the place of the air supply and exhaust passages 25 and 26 in the housing 1 of the previously described modification of the vibrator.
  • the hollow shaft 35 has radial openings 39, 40 and 41 through the wall thereof, to substitute for the openings 27, 28, 29 through the internal wall of the housing 1 of the previous embodiment for the same purpose.
  • the openings 39, 40 and 41 establish communication between the passages 37 and 38 within the hollow shaft 35 and the working spaces 13 and 14 through the axial passages (3 and 4), radial passages (42 and 43), tangential passages(7 and 8) and annular grooves (44 and 45) in the body of impact member 46.
  • the annular grooves 44 and 45 of this embodiment are for the same purpose as the annular grooves 9 and 10 in the impact member 2 of the previously described embodiment.
  • the hollow shaft 35 passes through the impact member 46, disc 48, resilient suspension member 49 and through upper end wall 47 of the housing 34 of the vibrator.
  • annular clearance K between the hollow shaft 35 and the above listed parts through which it passes, with the clearance preventing jamming of the impact member 46, as the latter reciprocates within the housing 34 along the hollow shaft 35, and providing forrocking of they disc 48 relative to the axis of symmetry thereof, resulting from the impacts of the impact member 46 upon this disc.
  • a socket 50 in the end wall 47 of the housing 34 accommodates an elastic pivot mount 51, with the hollow shaft 35 having the upper extremity thereof elastically mounted by means of this elastic pivot mount 51.
  • the latter serves additionally as a sealing means preventing bleeding of the compressed air from the upper working space 14, into atmosphere through the annular clearance K in operation of the vibrator.
  • the elastic pivot mount 51 is retained inthe axial direction by a washer 52 and a lock ring 53.
  • the projections 17 and 18 provided on the respective face ends of the impact member 46 are spaced farther from the axis of the impact member than in the previously described modification, which leads to an increased value of the torques M and M Therefore, the housing 34. is imparted transverse vibrations with a greater amplitude.
  • the air supply passage 37 and theair exhaust passage 38 being defined by means of longitudinal-partition36 within the hollow shaft 35, instead of the passages 25 and 26 serving the same purpose, provided invthe wall of the housing 1 of the previously described modifica-j tion, the thickness of the wall of the housing 34 can be substantially reduced, since in this case the thickness is selected to meet the strength. andabrasion wear requirements only. Consequently, the heaviestpart of the vibrator, its housing, can be substantially lighter, and thus the weightof the vibrator, as whole, can be reduced, which is essential for. a manually operated tool.
  • the profiled longitudinal partition 36 is preferably made from a material lighter than metal, e.g., by the hollow shaft being mountedin a mold in the course of the manufacture thereof, and the partition 36 being pressure-molded from a plastic material.
  • the body of impact member 54 (FIGS. l4and IS), a twodiameter bore 55 receiving therein a one-way valve.
  • the valve includes a ball-shaped valve member56, a spring 57 and a valve seat.58.
  • the latter has a bore 59 extending therethrough, through which andthe bore 55, the lower working space 13 communicates with the upper working space when the valve opens.
  • the pressure exerted by the spring 57 upon the valve member 56 is adjusted for the valve to open when the pressure within the working'space rises above themean rated pressure for the operation ofthe vibrator. With the valve thus adjusted, there prevented excessive bleeding of compressed air through the valve.
  • the one-way valve assembly in the impact member operates, as follows. As the impact member 54 is approaching the disc 20, there is produced intermediate of the impact member 54 and the end wall 22 of the housing 34, an air cushion wherein the air pressure is higher than the rated supply pressure. This air cushion presents a great resistance to the motion of the impact member 54 and, consequently, reduces the kinetic energy stored by the impact member during its movement from the disc 19. However, in this embodiment of the invention, this reduction, i.e., the influence of the air cushion on the impact energy of the impact member 54 is but minimal, since prior to the impact, the pressure in the working space 13 is reduced to the rated supply value by a portion of the compressed air being discharged therefrom via bore 55 (FIG.
  • a thin-walled protection cylinder (FIGS. 16 to 18), with there being mounted intermediate this cylinder and the internal .wall of the housing 34, a resilient member 61.
  • the resilient member 61 may be a corrugated'leaf spring positioned within the radial annular clearance M left intermediate of the intem al wall of the housing 34 and the thin-walled cylinder 60.
  • the protective cylinder 60 is mounted within the housing 34 intermediate of annular abutments 62 and 63 (FIG. 1S),v
  • each a rubber ring 64 sandwiched between two rigid rings 65.
  • the rings 65 contacting the ends of the cylinder 60 are preferably of an antifriction material, e.g., from graphite bronze.
  • the ring assemblies also serve to seal the working spaces 13 and 14, thus preventing leakage of compressed air into the annular clearance M, when the cylinder 60 is skewed relative to the axis of the housing 34 in operation.
  • transverse partition 66 (FIG. 19) dividing the internal space of the housing 34 into two chambers defining together with respective two impact members 67 and 68 received within these chambers, four working spaces 69, 70, 71 and 72.
  • the transverse partition 66 is in fact an intermediate additional end wall of the housing, having a pair of discs 73 and 74 mounted at the opposite sides thereof with the help of a double-sided tubular resilient suspension member 75.
  • the connection of the discs 73 and 74 with the wall 66 is thus similar to the connection of the discs 49 and 20 (FIG. 11), respectively, with the walls 21 and 22 (see above, FIG. 1), and the only difference is in the modified shape of the resilient suspension member.
  • the impact members 67 and 68 are provided, like the previously describedimpact member 2, with the off-center projections l7'and 18 on the opposite end faces thereof, adapted to deliver impacts upon the respective ones of the discs 73, 20, 48 and 74.
  • the impact members 67 and 68 are preferably designed-to have different frequencies of the impacts upon the respective discs 73, 20 and 48, 74; moreover, they may have different angular speeds of rotation about their respective axes.
  • the different frequencies of the impacts of the impact members 67 and 68 and the different speeds of their rotation can be attained by the members having different masses, different face end areas or different lengths of the strokes; alternatively, this can be effected by supplying different amounts of compressed air into the respective working spaces, or else by ensuring that the respective tangential passages 7 and 8 (FIGS. 3 and 4) have different flow passage areas.
  • the last-described embodiment is in fact a double vibrator offering low-frequency and high-frequency transverse vibrations due to the respective agitating forces P and also high-frequency and low-frequency transverse vibrations brought about by the centrifugal agitating forces F.
  • the last-described vibrator has variable vibration parameters, such as the frequency of the impacts, the agitating force, the amplitude of the transverse vibrations, with these parameters varying automatically owing to the inherent structure of the vibrator.
  • a pneumatic vibrator comprising: a housing including a closed cylinder; an impact member mounted for reciprocation within said housing, said member having opposite end faces and passages in the body thereof and annular grooves in the peripheral surface thereof for the passage of compressed air; compressed air distributing means, two impact-receiving members for imparting additional transverse vibrations to said housing, said two impact-receiving members being mounted within said housing with radial and axial clearances therefrom, adjacent to the opposite end walls of said housing and connected with said end walls; striking means for delivering impacts upon said impactreceiving members at the points thereof remote from the axes of said impact-receiving members, said striking means being defined by off-center projections on the respective opposite end faces of said impact member, adapted to engage said impact-receiving members at the successive impacts of said impact member.
  • said impact member in order to obtain additional circular transverse vibrations, said impact member has tangential passages in said body thereof, for effecting rotation of said impact member about the axis thereof under the action of compressed air issuing from said tangential passages, and said tangential passages having their respective inlets and outlets disposed within said annular grooves.
  • a one-way valve means is mounted in said body of said impact member, adapted to open when the pressure in the working space rises above the rated supply pressure value.
  • a pneumatic vibrator comprising: a housing including a cylinder with closed opposite ends, said cylinder divided into two adjacent internal chambers by at least one transverse partition sewing as an end wall for said two adjacent internal chambers, impact members mounted for reciprocation, respectively, in each one of said adjacent internal chambers, each said impact member having opposite end faces and passages in the body thereof and annular grooves in the peripheral surface thereof for the passage of compressed air; an air distributor; discs mounted in each said chamber adjacent to said end walls, with radial and axial clearances, said discs being resiliently connected with said respective end walls, and said discs being adapted to impart additional transverse vibrations to said housing; said impact members having projections located eccentrically on the respective opposite end faces thereof for delivering impacts upon the portions of said discs, remote from the axes of said discs, with said projections engaging said discs at the impacts of said impact members.
  • said impact members have each tangential passages in the bodies thereof, for effecting rotation of said impact members about their respective axes under the action of compressed air issuing from said tangential passages, with said tangential passages having their respective inlets and outlets disposed within said annular grooves.

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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)
US00172421A 1970-12-22 1971-08-17 Pneumatic vibrator Expired - Lifetime US3726508A (en)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
SU1602014A SU324789A1 (ru) 1970-12-22 Пневматический вибратор
SU1618402A SU357009A1 (ru) 1971-02-23 ПНЕВМАТИЧЕСКИЙ ВИБРАТОРi;i.L,>&-:.^.'^. •;-..-:. ,-.-^^^ :i 1Г!';'^'-ЙТ»"--.'--''^"^' •""•' '•"'"iCJi i,fj J и;-.' i ...л г.'. ,;, :''•::;•йИБ;ШОГгч{д у
SU1618405A SU325770A1 (ru) 1971-02-23 Пневматический вибратор
SU1618404A SU338029A1 (ru) 1971-02-23 Пневматический вибратор
SU1618403A SU338030A1 (ru) 1971-02-23 Пневматический вибратор

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US00172421A Expired - Lifetime US3726508A (en) 1970-12-22 1971-08-17 Pneumatic vibrator

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US (1) US3726508A (enrdf_load_stackoverflow)
DE (1) DE2139907A1 (enrdf_load_stackoverflow)
FR (1) FR2119313A5 (enrdf_load_stackoverflow)
SE (1) SE360993B (enrdf_load_stackoverflow)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5198246A (en) * 1990-09-27 1993-03-30 Monoform, Inc. Concrete molding device
US5209564A (en) * 1992-01-21 1993-05-11 National Air Vibrator Company Vibrator
US20040055744A1 (en) * 2001-03-01 2004-03-25 Shunfeng Zheng Method and apparatus to vibrate a downhole component
US20090272255A1 (en) * 2008-05-01 2009-11-05 Hansen Robert A Vibrator
CN112832532A (zh) * 2021-01-06 2021-05-25 全椒县通达交通建设工程有限公司 一种建筑施工用插入式振动棒

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1525955A (en) * 1975-02-17 1978-09-27 Vibratechniques Ltd Vibrators
CN112377212B (zh) * 2020-09-30 2022-12-13 诸暨市辉煌五金有限公司 隧道台车振动棒

Citations (4)

* 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
US3162426A (en) * 1961-06-23 1964-12-22 Vibratechniques Sa Vibrator
US3460808A (en) * 1966-06-23 1969-08-12 Dart Mfg & Sales Co Apparatus and method for generating vibrations
US3650509A (en) * 1970-09-29 1972-03-21 Malan Vibrator Co Inc Free rotor vibrator

Patent Citations (4)

* 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
US3162426A (en) * 1961-06-23 1964-12-22 Vibratechniques Sa Vibrator
US3460808A (en) * 1966-06-23 1969-08-12 Dart Mfg & Sales Co Apparatus and method for generating vibrations
US3650509A (en) * 1970-09-29 1972-03-21 Malan Vibrator Co Inc Free rotor vibrator

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5198246A (en) * 1990-09-27 1993-03-30 Monoform, Inc. Concrete molding device
US5209564A (en) * 1992-01-21 1993-05-11 National Air Vibrator Company Vibrator
US20040055744A1 (en) * 2001-03-01 2004-03-25 Shunfeng Zheng Method and apparatus to vibrate a downhole component
US6907927B2 (en) * 2001-03-01 2005-06-21 Schlumberger Technology Corporation Method and apparatus to vibrate a downhole component
US20090272255A1 (en) * 2008-05-01 2009-11-05 Hansen Robert A Vibrator
US7963207B2 (en) * 2008-05-01 2011-06-21 Dynamil Air Inc. Vibrator
CN112832532A (zh) * 2021-01-06 2021-05-25 全椒县通达交通建设工程有限公司 一种建筑施工用插入式振动棒

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Publication number Publication date
DE2139907A1 (de) 1972-07-06
SE360993B (enrdf_load_stackoverflow) 1973-10-15
FR2119313A5 (enrdf_load_stackoverflow) 1972-08-04

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