US3885883A - Method and apparatus for compacting earth, sand, gravel, ballast and similar materials - Google Patents

Method and apparatus for compacting earth, sand, gravel, ballast and similar materials Download PDF

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US3885883A
US3885883A US343482A US34348273A US3885883A US 3885883 A US3885883 A US 3885883A US 343482 A US343482 A US 343482A US 34348273 A US34348273 A US 34348273A US 3885883 A US3885883 A US 3885883A
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pressure
compacting
tool
time
hydraulic cylinder
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English (en)
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Helmut Sieke
Rainer Sieke
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    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
    • E02D3/00—Improving or preserving soil or rock, e.g. preserving permafrost soil
    • E02D3/02—Improving by compacting
    • 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

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  • the time-pressure curve representing pressure of the tool on the material being compacted is not sinusoidal but has a shape representing an initial sudden increase in pressure, maintenance of pressure for a selected period of time thereafter and finally a rapid decrease of pressure to a low value.
  • the period during which pressure is maintained after the initial push is long enough to permit the material to become stabilized in a compacted state so that it does not spring back materially when the pressure is released.
  • Apparatus for carrying out the method comprises a hydraulic cylinder.
  • a fluid pressure system and continuously operating value means controlling the supply of pressure fluid to and discharge of pressure fluid from the hydraulic cylinder to provide the desired nonsinusoidal time-pressure curve.
  • the present invention relates to a process and apparatus for compacting earth, sand, gravel, ballast and similar materials or mixtures thereof by means of compacting apparatus having a reciprocating compacting tool.
  • the reciprocation of compacting tools is generally produced mechanically for example by rotating weights or eccentrics which act on the compacting tool.
  • Such reciprocation exhibits a very strong sinusoidal form.
  • Usually weaker vibrations are superimposed on the basic sinusoidal form.
  • Operation of the compacting tool with reciprocation of sinusoidal form has the disadvantage that the material to be compacted is energized sinusoidally which can lead to the effect that the material particles recoil back from their compacted position so that optimal compacting in minimum time is not achieved.
  • the present invention avoids this difficulty and makes possible optimum compacting of the material in minimum time.
  • the compacting tool at the beginning of a stroke is given a strong push through which high pressure is exerted on the mass to be compacted and after the initial push pressure is maintained for a selected interval of time on the material after which the pressure is relieved.
  • an intentionally nonsinusoidal oscillation is employed in order first to exert a strong pressure on the mass to be compacted and thereafter to maintain the mass under pressure for a long time so that the forwardly pushed portions of material cannot immediately spring back to another position but are stabilized and held as much as possible in the compacted position.
  • the pressure after the initial push can remain the same or it can increase or decrease as desired.
  • the continuing pressure can act in a direction other than the direction of the initial push.
  • This compacting cycle can be part of another compacting operation.
  • FIGS. 1, 2, 3 and 4 are different force-time diagrams in which the coordinate A represents force or pressure applied to the work and the coordinate B represents time;
  • FIGS. 5, 6 and 7 are schematic illustrations of compacting apparatus for carrying out the method in accordance with the invention.
  • FIG. 8 is a schematic view illustrating the use of apparatus in accordance with the invention to compact the ballast of a railway road bed.
  • FIGS. 1 to 4 illustrate schematically several different waveforms representing the force-time curves of compacting apparatus operating in accordance with the present invention.
  • the ordinates represent the force or pressure exerted by the compacting tool on the material being compacted while the abscissae represent time.
  • FIG. 1 there is shown a substantially rectangular waveform which can, for example be obtained with hydraulically driven compacting apparatus.
  • the pressure rises suddenly from an initial low pressure P1 to a high pressure P2. After the peak P2, the pressure drops back slightly to a high pressure P3 at which it is maintained for a selected period of time at the end of which the pressure is suddenly reduced to the initial value Pl.
  • the waveform is trapezoidal and represents progressively increasing force after the initial push.
  • the pressure rises suddenly from an initial low pressure P1 to a value P2 and then rises progressively at a selected uniform rate to a still higher pressure P3 during a selected period of time at the end of which the pressure drops suddenly back to the initial pressure PI.
  • This can also be obtained with hydraulically driven equipment.
  • the waveform is also trapezoidal but with progressively decreasing force after the initial push.
  • the pressure rises suddenly from an initial low pressure P1 to a high pressure P2 and then decreases slowly at a selected uniform rate to an intermediate pressure P3 during a selected period of time at the end of which the pressure drops suddenly back to the initial value Pl.
  • This waveform can also be obtained with hydraulically or pneumatically operated equipment.
  • FIG. 4 illustrates another waveform representing an initial strong push with a lesser pressure exerted thereafter.
  • the pressure rises suddenly from an initial value PI to a peak high pressure P2 and then drops back quickly to an intermediate value P3 at which it is maintained substantially uniform for a selected period of time at the end of which the pressure drops suddenly back to the initial pressure Pl.
  • This can be obtained mechanically through movement of a rammer which is first catapulted against the material to be compressed and thereafter remains resting on the material for a period of time until it is mechanically withdrawn. It can also be obtained by hydraulically operated apparatus.
  • Nonsinusoidal waveforms such as those illustrated by way of example in FIGS. 1 to 4 can be generated by suitable mechanical, hydraulic, pneumatic or electro-mechanical equipment. Suitable hydraulically operated means for producing waveforms like those shown in FIGS. 1 to 4 is illustrated schematically in FIGS. 5 to 7.
  • Hydraulically operated apparatus for producing a time-pressure curve such as that shown in FIG. I is illustrated schematically in FIG. 5.
  • the apparatus is shown as comprising a rotary pressure pump 1 which pumps hydraulic oil under pressure from a storage tank 2 to a rotary control valve 3. From here the hydraulic oil is delivered through a conduit 4 to a working cylinder 5 in which a piston 7 connected with a suitable compacting tool is reciprocable.
  • the piston 7 is movable toward the right as viewed in FIG. 5 by oil pressure in the cylinder 5 and is moved toward the left by a return spring 6.
  • the control valve 3 comprises a casing 3A in which a valve member in the form of a rotor 38 is rotatable and is driven at selected constant speed in the direction indicated by the arrows.
  • the casing 3A is provided with ports communicating respectively with the conduit 4 leading from the control valve to the working cylinder 5, a conduit 4A leading from the pump 1 to the control valve 3 and two oppositely disposed return conduits 10 leading from the control valve 3 back to the storage tank 2.
  • the valve rotor 33 has a diametrically disposed channel 8 for connecting conduit 4A with conduit 4 when the rotor is in proper position to supply pressure fluid from the pump 1 to the working cylinder 5.
  • T-shaped channels 9 which are symmetrically disposed and each of which comprises a first channel portion parallel to but spaced from the channel 8 and a second channel portion which is per pendicular to the first channel portion at its midpoint.
  • Each of the T-shaped channels 9 is arranged to connect the conduit 4 from the working cylinder to both of the return conduits 10 when the valve rotor is in proper position.
  • a conduit 48 branching off of the conduit 4 between the control valve 3 and the working cylinder 5 leads to the lower part of a pressure reservoir 11 which comprises a closed vessel divided by a central flexible diaphragm or membrane 11A into an upper chamber containing 2' under pressure and a lower chamber which is connected by the branch conduit 43 to the conduit 4 and is adapted to receive pressure oil from the conduit 4.
  • the gas in the upper chamber of the pressure reservoir 11 is under a pressure of the same order of magnitude as the pressure produced by the pressure pump 1.
  • the apparatus illustrated in FIG. 5 works in the following manner.
  • the pump l is continuously driven and constantly provides a supply of hydraulic oil under substantially constant high pressure through the conduit 4A to the control valve 3.
  • the rotor 38 of the control valve is rotated continuously in the direction indicated by the arrows.
  • pressure fluid flows through the channel 8 and the conduit 4 into the working cylinder 5 and also through conduit 48 into the pressure reservoir 11.
  • the pressure fluid thus supplied to the working cylinder 5 drives the piston 7 which is connected with the compacting tool toward the right as viewed in FIG. 5, thereby compressing the spring 6.
  • the diaphragm 11A of the pressure reservoir 11 is deflected upwardly thereby compressing the gas in the upper chamber of the pre ssure reservoir.
  • the conduit 4 is closed and hence any changes or movements can occur only within the closed system comprising the conduits 4 and 4B, the working cylinder 5 and the pressure reservoir 11. Any such changes or movements are of a relatively limited nature. After the gressure peak upon the introduction of pressure fluid into the system there is only a very slight backward m vement of the piston 7 by the force of the spring 6 upc l equalization of pressure in the sys tem and perhaps tome slight additional flow into the pressure reservoir 11.
  • the pressure in the cylinder 5 is m: intained substantially constant since any small losses that may occur are compensated for by the pressure reserioir 11. This pressure is maintained until the valve rotvr 3B has turned approximately 90 to bring the perpendicular stem portion of one of the T-shaped channels 9 into alignment with the port of the conduit 4 whereupon the hydraulic oil is discharged from the working cylinder 5 and the pressure reservoir 11 through both of the return conduits 10 to the storage tank 2. The pressure in the working cylinder 5 is thereupon suddenly reduced so that the piston 7 is moved to the left by the spring 6.
  • the operating cycle of the apparatus of FIG. 5 is continually repeated through the following phases:
  • the system comprising the working cylinder 5 and pressure reservoir 11 is closed off so that the pressure in the system remains substantially constant and pressure of the compacting tool on the material being compacted is maintained during a selected period of time.
  • the working cylinder 5 and pressure reservoir 11 are connected to the return conduits l0 whereupon pressure fluid is discharged to the storage tank 2. It will be seen that with the channels of the valve rotor disposed as shown in FIG. 5, pressure is maintained in the working cylinder 5 for approximately one half of the cycle of operation. The period during which pressure is maintained can be increased or decreased by moving the stem portion of the T-shaped channel 9 in one direction or the other.
  • FIG. 6 Apparatus for hydraulically operating a compacting tool in accordance with the time-pressure curve of FIG. 2 is illustrated schematically in FIG. 6.
  • This apparatus likewise comprises a pressure pump 1, an oil storage tank 2, a rotary control valve 3, a conduit 4 leading from the control valve to a hydraulic working cylinder 5 in which a piston 7 is reciprocable and is provided with a return spring 6.
  • the rotor 35 of the control valve 3 is different in that a recess 8A is pro vided in the periphery of the rotor at each end of the channel 8 and extends circumferentially from the respective end of the channel 8 in a direction opposite to the direction of rotation of the valve rotor.
  • each of the recesses 8A can be se lected as desired but the recesses are shown by way of example in FIG. 6 as extending almost to the discharge channels 9.
  • the discharge channels 9 are also different from those shown in FIG. 5 in that they are L-shaped instead of T-shaped and there is only a single discharge conduit which opens into the valve casing 3A in such position as to communicate with one leg of the channel 9 when the other leg is in registry with the conduit 4 leading from the control valve 3 to the working cylinder 5.
  • the pressure reservoir 11 is also differently arranged in that it is connected by a branch conduit 48 with the conduit 4A leading from the pressure pump 3 to the control valve 3.
  • the apparatus shown in FIG. 6 works in the following manner.
  • the pressure pump 1 continually provides a supply of pressure fluid.
  • the pump 1 supplies pressure fluid only to the pressure reservoir 11.
  • a sudden flow ofpressure fluid from the pressure reservoir 11 and from the pressure pump 1 into the working cylinder 5 occurs.
  • a rapid increase of pressure in the working cylinder 5 occurs and the piston 7 is moved rapidly toward the right thereby compressing the spring 6.
  • the pressure pump 1 As the pressure pump 1 continues to work, it delivers pressure fluid not only to the pressure reservoir 11 but also to the working cylinder 5.
  • the pressure in the working cylinder 5 is thereby progressively increased. This continues until the valve rotor 38 has rotated so that the recesses 8A are no longer in communication with the conduits 4 and 4A. At this instant the increase in pressure ceases. However, shortly thereafter a connection is established by the channel 9 between the conduit 4 leading to the working cylinder 5 and the discharge conduit 10 so that pressure fluid is discharged out of the working cylinder 5 through the conduit 4, channel 9 and conduit 10 into the storage tank 2.
  • the pressure in the working cylinder 5 thereby decreases to a low value.
  • the piston 7 is thereby unloaded and is moved toward the left by the return spring 6.
  • the pressure pump operates after emptying of the pressure reservoir to supply pressure fluid to the working cylinder and to the pressure reservoir, thereby producing a progressively increasing pressure in the working cylinder during a selected period of time.
  • the period can be decreased by decreasing the circumferential extent of the recesses 8A so that the pressure would be progressively increased until the ends of the recesses 8A reach the ports of conduits 4 and 4A whereupon the conduit 4 would be closed so as to maintain substantially constant pressure in the cylinder 5 until the discharge channel 9 of the valve rotor reaches the port of the conduit 4.
  • the circumferential extent of the recesses 8A can be increased so as to lengthen the period of time that pressure in the working cylinder 5 is progressively increased.
  • FIG. 7 there is shown a further embodiment of the apparatus suitable for realizing the time pressure curve of the kind shown in FIG. 3.
  • a pressure pump 1 a storage tank 2, a control valve 3, a working cylinder 5 connected with the control valve by a conduit 4 and a piston 7 reciprocable in the cylinder and biased in one direction by a spring 6.
  • a return conduit 10 and a pressure reservoir 11. Differences reside in the form of the rotor 3B of the control valve 3 and in the connection of the pressure reservoir 11 with the control valve.
  • the pressure reservoir 11 is connected with a separate port provided in the casing 3A of the control valve slightly in advance of the port of the conduit 4 connecting the control valve with the working cylinder 5 and in position to be in the path of movement of the channels 8 and 9.
  • valve 12 which throttles flow of liquid into the reservoir but permits quick emptying of the reservoir.
  • the valve 12 can for example comprise a conical chamber comprising a ball which is movable toward the narrow end of the chamber by flow of oil in a direction toward the pressure reservoir so as to restrict the flow while being movable toward the larger end of the chamber by flow of oil in the opposite direction so that oil can flow out of the pressure reservoir rapidly.
  • the rotor 38 of the control valve 3 is provided with a diametrically disposed channel 8 which connects the pressure pump 1 with the working cylinder 5 when it is aligned with the ports of the conduits 4 and 4A. Moreover, there are two L-shaped channels 9 for connection with the return conduit 10. The rotor of the valve 3 is further provided with opposite circumferentially ex tending recesses B which are disposed between respective ends of the channels 8 and 9 and serve to provide a connection between the conduit 4 leading to the working cylinder 5 and the conduit 48 leading to the pressure reservoir 11. These recesses are not connected either with channel 8 or with the channels 9. Furthermore.
  • the port of the valve casing connected with the return conduit 10 is enlarged by a recess C which extends circumferentially in a direction opposite to the direction of rotation of the valve rotor a distance corresponding approximately to the spacing of the valve ports for the conduits 4 and 4B respectively.
  • the apparatus illustrated in FIG. 7 works as follows.
  • the pump 1 is operated continuously to supply oil pressure and the rotor 38 of the control valve is continu' ously rotated in the direction indicated by the arrows.
  • the channel 8 of the valve rotor comes into alignment with the ports of conduits 4 and 4A, pressure fluid from the pump 1 flows rapidly through conduit 4A, channel 8 and conduit 4 to the working cylinder 5 thereby producing a sudden increase in pressure in the working cylinder and moving the piston 7 to the right thereby compressing the spring 6.
  • the recess 8 of the valve rotor comes into communication with the conduit 4 thereby connecting the working cylinder 5 with the pressure reservoir 11 through the conduit 4, recess B and conduit 48.
  • the pressure fluid can thereby flow from the cylinder 5 to the pressure reservoir 11. However, flow is restricted by the valve 12 so that there is only a gradual and progressive decrease of pressure in the cylinder 5. This continues until the trailing end of the recess B passes the port of the conduit 48. Shortly thereafter the return channel 9 of the valve rotor comes into communication with the port of the conduit 43 so that pressure fluid is discharged from the pressure reservoir to conduit 48, channel 9 and conduit to the storage tank 2. When the return channel 9 reaches the port of conduit 4, pressure fluid remaining in the cylinder 5 is discharged rapidly through the con duit 4, channel 9 and conduit 10 thereby producing a sudden drop in pressure to a low value.
  • the enlarge ment of the port of conduit 10 by the circumferentially extending recess C provides for communication of the channel 9 with the conduit 10 when the channel 9 is in communication with the port of the conduit 48 as well as with the port of the conduit 4.
  • the piston 7 Upon the sudden decrease of pressure in the working cylinder 5 the piston 7 is returned to the left by the spring 6.
  • the rate of decrease of pressure with the apparatus and method of the present invention as illustrated in FIGS. 3 and 7 is substantially constant so that the progressive decrease in pressure is represented by a straight line.
  • the rate of decrease of pressure and hence the slope of the line are controlled by the throttling valve 12 which regulates flow of pressure fluid from the working cylinder 5 to the pressure reservoir 11 during the time that the recess B of the valve rotor is in communication with the ports of conduits 4 and 4B.
  • the rate of decrease can thus be increased or decreased by decreasing or increasing the resistance provided by the throttling valve 12.
  • the length of the period during which pressure in the working cylinder is progressively decreased after the initial sudden increase is controlled by the length of the recess B in the rotor 3B of the control valve. Thus, within the limits of design of the valve this period can be increased or decreased. If the recess B is made shorter at its lead ing end, pressure in the cylinder 5 will be maintained at a substantially constant value for a period of time following the sudden pressure increase and thereafter will decrease progressively during the time that the recess B provides communication between conduits 4 and 48. If the recess B is shortened at its trailing end the pressure time curve will have a substantially horizontal portion following the downward slope and prior to the finaal sudden decrease in pressure.
  • pressure pumps of different capacities can be used and that the pressure reservoirs 11 can also be of different sizes according to the bore and stroke of the working cylinder 5, the volumetric capacity and pressure characteristics of the pump and the desired operating characterstics of the apparatus.
  • the time-pressure curve shown in FIG. 4 can also be obtained with apparatus such as that illustrated in FIG. 7 by omitting the throttling valve 12 in the conduit 48 between the control valve 3 and the pressure reservoir 11.
  • pressure in the working cylinder rises rapidly as previously described when the channel 8 of the control valve provides communication between conduits 4A and 4.
  • the recess B of the control valve rotor comes into communication with the ports of conduits 4 and 4B, pressure fluid flows rapidly from the working cylinder 5 to the pressure reservoir 11 until pressure in the closed system comprising the cylinder 5, conduits 4 and 4B and the pressure reservoir 11 is equalized. This results in a sudden drop of pressure in the cylinder 5 to a level intermediate minimum and maximum pressures in the working cylinder.
  • the level to which the pressure drops can be controlled by varying the respective capacities of the pressure reservoir 11 and the working cylinder 5. If the pressure reservoir is made smaller, the pressure drop will be less and conversely a larger pressure drop results from the provision of a larger pressure reservoir.
  • the return channel 9 reaches the port of conduit 4B, pressure fluid is discharged from the pressure reservoir 1 1, which is no longer in communication with the working cylinder 5.
  • the return channel 9 reaches the port of conduit 4
  • pressure fluid is rapidly discharged from the working cylinder 5 through conduit 4, channel 9 and conduit 10 to the storage tank 2 thereby producing a final decrease of pressure to a low value.
  • the timepressure curve illustrated in FIG. 4 is thereby procluced.
  • pressure is maintained by the compacting tool on the material being compacted during a selected period of time after the initial sudden application of high pressure.
  • the pressure may be maintained approximately constant as illustrated in FIG. 1, may progressively increase as illustrated in FIG. 2, may progressively decrease to an intermediate value as illustrated in FIG. 3 or, as is illustrated in FIG. 4, it may drop quickly to an intermediate value which is maintained throughout the selected period.
  • the length of the period of time during which pressure is maintained can be varied as desired.
  • the period of time during which pressure is maintained should be long enough to permit the material being compacted to stabilize in its compacted state so that it will not bounce back after release of pressure.
  • the period of time during which pressure is maintained is at least one quarter of a complete cycle of operation of the compacting tool. In the embodiments illustrated by way of example in the drawings, the period is equal to approximately one half of the working cycle.
  • FIG. 8 shows schematically a practical application of the apparatus shown by way of example in FIGS. 5 to 7.
  • compacting tools 13 are shown compacting the ballast bed 14 supporting the ties l5 and rails 16 of a railway line.
  • the compacting tools 13 have working ends of stepped pyramid form and are shown as being operated to compact the ballast underneath the ties.
  • the compacting tool is actuated by two hydraulic cylinders such as are illustrated in FIGS. 5 to 7, one of the cylinders being arranged to move the compacting tool vertically and the other being arranged to move it horizontally.
  • the rotors of the control valves of the respective hydraulic cylinders are out of phase relative to one another, for example by 45, so that after the compacting tool has been moved downwardly by one cylinder and while it is still held in pressure contact with the ballast, the tool is moved horizontally by the other hydraulic cylinder. In this manner effective tamping of the ballast underneath the ties can be effected in a very short time.
  • the rotors of both control valves can be arranged on the same shaft so as to maintain the selected phase relation between them.
  • FIGS. 5 to 8 there is illustrated apparatus suitable for carrying out the method herein described and illustrated in FIGS. 1 to 4, it will be understood that other apparatus operated for example hydraulically, pneumatically, mechanically or electro-mechanically may be used if desired. Moreover, modifications can be made in the apparatus illustrated in FIGS. 5 to 8 while still maintaining essentially the same mode of operatron.
  • a process for compacting earth, sand, gravel, ballast and similar material which comprises subjecting a selected small area of sand material at a time to a periodic succession of individual pressure thrusts by means of a rectilinearly reciprocating compacting tool which is reciprocated cyclically but non-sinusoidally, the compacting tool at the beginning of each cycle being given a strong push through which a strong compacting pressure thrust is exerted on said material and pressure being thereafter maintained on said material by said tool for a selected period of time not less than one quarter of a cycle to hold the compacted material in place and thereby allow time for it to become settled and fixed in compacted condition, whereupon the pressure of said compacting tool on said material is relieved to complete the cycle, and thereupon repeating the cycle.
  • a process for compacting earth, sand, gravel, ballast and like material which comprises subjecting a selected small area of said material to a periodic succession sion of individual pressure thrusts by a compacting tool reciprocated rectilinearly cyclically but nonsinusoidally by a hydraulic cylinder, said process comprising providing a continuous supply of hydraulic fluid under predetermined pressure for operating said hydraulic cylinder and cyclically controlling the supply of said pressurized hydraulic fluid to and discharge of said fluid from said cylinder to actuate said compacting tool, each cycle comprising:

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  • Engineering & Computer Science (AREA)
  • Structural Engineering (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Soil Sciences (AREA)
  • Agronomy & Crop Science (AREA)
  • General Life Sciences & Earth Sciences (AREA)
  • Mechanical Engineering (AREA)
  • Paleontology (AREA)
  • Environmental & Geological Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)
  • Crushing And Grinding (AREA)
  • Machines For Laying And Maintaining Railways (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Percussive Tools And Related Accessories (AREA)
US343482A 1972-03-21 1973-03-21 Method and apparatus for compacting earth, sand, gravel, ballast and similar materials Expired - Lifetime US3885883A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE19722213577 DE2213577C3 (de) 1972-03-21 Vorrichtung zum Verdichten von Erd-, Sand-, Kies-, Schotter- und ähnlichen Massen

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US (1) US3885883A (is)
JP (1) JPS5753490B2 (is)
AT (1) AT344779B (is)
CH (1) CH571124A5 (is)
FR (1) FR2177372A5 (is)
GB (1) GB1429332A (is)
SE (1) SE401000B (is)

Cited By (7)

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US3981247A (en) * 1974-05-09 1976-09-21 Franz Plasser Bahnbaumaschinen-Industrie-Gesellschaft M.B.H. Track working machine with vibratory and reciprocable track working tools
US4068595A (en) * 1975-11-17 1978-01-17 Graystone Corporation Track tamper
US4092903A (en) * 1975-11-17 1978-06-06 Graystone Corporation Vibratory drive mechanism
US4127351A (en) * 1975-12-01 1978-11-28 Koehring Gmbh - Bomag Division Dynamic soil compaction
US4382715A (en) * 1979-07-17 1983-05-10 Koehring Gmbh - Bomag Division Mass compensated impacting apparatus
CN108204915A (zh) * 2017-11-23 2018-06-26 韦翠花 一种改进型生物实验用土壤压碎器
CN112176803A (zh) * 2020-09-30 2021-01-05 中电建路桥集团有限公司 提高砂性土在路床中的压实度进而降低路基沉降的方法

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DE2926117C2 (de) * 1979-06-28 1982-08-26 Lindauer Dornier-Gesellschaft Mbh, 8990 Lindau Von außen gehaltener zylindrischer Breithalter für Schlauchware
GB2071720B (en) * 1979-10-22 1983-10-05 Heliot Maurice Ets Stretcher for tubular knitted fabric
US5114355A (en) * 1990-05-04 1992-05-19 Amp Incorporated Right angle impedance matched electrical connector
US5116239A (en) * 1990-06-14 1992-05-26 Amp Incorporated Multiconductor flat cable connector, apparatus and method
EP0514055B1 (en) * 1991-05-13 1997-01-02 Fujitsu Limited Impedance-matched electrical connector
US5120232A (en) * 1991-08-06 1992-06-09 Amp Incorporated Electrical connector having improved grounding bus bars
US6857899B2 (en) 1999-10-08 2005-02-22 Tensolite Company Cable structure with improved grounding termination in the connector
US6217372B1 (en) 1999-10-08 2001-04-17 Tensolite Company Cable structure with improved grounding termination in the connector
US6428344B1 (en) 2000-07-31 2002-08-06 Tensolite Company Cable structure with improved termination connector
CN113906363A (zh) * 2019-06-11 2022-01-07 株式会社岛津制作所 超临界流体装置及超临界流体装置的压力控制方法

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US2043585A (en) * 1933-07-26 1936-06-09 City Of Detroit Concrete tamping device
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US2254744A (en) * 1939-08-11 1941-09-02 Jackson Corwill Tamping machine or apparatus
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US2633782A (en) * 1950-10-19 1953-04-07 Clyde H Clement Cement tamping machine
US2821935A (en) * 1952-05-03 1958-02-04 Theodore S Bean Ballast tamper
US2909106A (en) * 1953-08-17 1959-10-20 Berrange Aubrey Ralph Impact rolling or tamping machines for the compaction of loose materials, such as road surfaces
US3621786A (en) * 1970-04-22 1971-11-23 Ivan L Joy Railway ballast tamper
US3625156A (en) * 1969-09-05 1971-12-07 Jackson Vibrators Ballast tamping workhead
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US1731014A (en) * 1927-10-18 1929-10-08 Thomas J Lavan Track ballasting
US2043585A (en) * 1933-07-26 1936-06-09 City Of Detroit Concrete tamping device
US2084983A (en) * 1933-09-05 1937-06-29 Baily Robert William Apparatus for kneading and working plastic material
US2254744A (en) * 1939-08-11 1941-09-02 Jackson Corwill Tamping machine or apparatus
US2633782A (en) * 1950-10-19 1953-04-07 Clyde H Clement Cement tamping machine
US2821935A (en) * 1952-05-03 1958-02-04 Theodore S Bean Ballast tamper
US2909106A (en) * 1953-08-17 1959-10-20 Berrange Aubrey Ralph Impact rolling or tamping machines for the compaction of loose materials, such as road surfaces
US3675581A (en) * 1969-07-24 1972-07-11 Plasser Bahnbaumasch Franz Mobile track tamping machine
US3625156A (en) * 1969-09-05 1971-12-07 Jackson Vibrators Ballast tamping workhead
US3621786A (en) * 1970-04-22 1971-11-23 Ivan L Joy Railway ballast tamper

Cited By (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3981247A (en) * 1974-05-09 1976-09-21 Franz Plasser Bahnbaumaschinen-Industrie-Gesellschaft M.B.H. Track working machine with vibratory and reciprocable track working tools
US4068595A (en) * 1975-11-17 1978-01-17 Graystone Corporation Track tamper
US4092903A (en) * 1975-11-17 1978-06-06 Graystone Corporation Vibratory drive mechanism
US4096806A (en) * 1975-11-17 1978-06-27 Graystone Corporation Track tamper with hingeable unitary pivotable tamping unit
US4127351A (en) * 1975-12-01 1978-11-28 Koehring Gmbh - Bomag Division Dynamic soil compaction
US4382715A (en) * 1979-07-17 1983-05-10 Koehring Gmbh - Bomag Division Mass compensated impacting apparatus
CN108204915A (zh) * 2017-11-23 2018-06-26 韦翠花 一种改进型生物实验用土壤压碎器
CN112176803A (zh) * 2020-09-30 2021-01-05 中电建路桥集团有限公司 提高砂性土在路床中的压实度进而降低路基沉降的方法

Also Published As

Publication number Publication date
GB1429332A (en) 1976-03-24
JPS5753490B2 (is) 1982-11-13
DE2213577B2 (de) 1975-08-07
CH571124A5 (is) 1975-12-31
AT344779B (de) 1978-08-10
DE2213577A1 (de) 1973-10-18
FR2177372A5 (is) 1973-11-02
JPS496543A (is) 1974-01-21
SE401000B (sv) 1978-04-17
ATA244973A (de) 1977-12-15

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