US3834827A - Vehicle mounted vibratory compactor - Google Patents

Vehicle mounted vibratory compactor Download PDF

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Publication number
US3834827A
US3834827A US00178567A US17856771A US3834827A US 3834827 A US3834827 A US 3834827A US 00178567 A US00178567 A US 00178567A US 17856771 A US17856771 A US 17856771A US 3834827 A US3834827 A US 3834827A
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compacting
vibrating element
rod
compacting machine
vibrating
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US00178567A
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English (en)
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A Linz
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Individual
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Individual
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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
    • E02D3/046—Improving by compacting by tamping or vibrating, e.g. with auxiliary watering of the soil
    • E02D3/068—Vibrating apparatus operating with systems involving reciprocating masses

Definitions

  • ABSTRACT A vehicle mounted vibratory compactor employing a pair of vibrating elements that extend laterally across the entire width of the vehicle and are mounted, as a unit, in a rigid support frame.
  • the frame is designed as a parallelogram with parallel control arms for resisting the bending forces applied thereto by the action of the vibrating elements compressing materials, such as soils of all types, and the reactive forces of the materials.
  • the frame is movable vertically within guides defined on the vehicle so that the vibrating elements can be elevated sufficiently to avoid contacting road obstacles as the vehicle is moved to the work site, and lowered variable amounts to alter the amplitude of the movement of the vibrating elements.
  • the magnitude of the compression forces exerted by the vibrating elements is varied considerably by the utilization of diverse combinations of springs, reciprocal plates, pressure limit valves, pneumatic servomechanisms, pistons, and the like, which determine the natural fre quency of the compactor system and thus control the resonant frequencies at which the maximum compressive forces are produced.
  • the vibrating elements which may assume the form of plates, rollers, beams or shoes, may be fabricated from a plurality of simplified components. If desired, she epsfoot projections may be formed on the bottom surface of the vibrating elements.
  • VEHICLE MOUNTED VIBRATORY COMPACTOR BACKGROUND OF THEv INVENTION 1.
  • the invention relates generally to. vehicle mounted vibratory compactors, and more particularly to vertically adjustable rigid frames thatsupport a pair of cooperating vibrating elements for efficient compacting operation. 2.
  • Vibratory compactors of various designs have been widely used for compacting particulate materials, such as sand, gravel, soils of all kinds and consistencies, by repeatedly and rapidly applying vibratory compacting forces thereto.
  • One variety of conventional vibratory compactors has'included a vehicle frame, a motor for driving the frame to the work site, a transverse shaft supported onthe vehicle frame, an array of heavy tamping shoes suspended from the shaft at spaced intervals, and take-off belts for delivering vibratory energy from the motor to each of the tamping shoes in sequence.
  • Such multishoe vibratory compactors are disclosed in several: United States patents, including US. Pat. No. 2,938,438, granted to W. L. Hamilton, US. Pat. No. 2,958,268, granted toMoir, and US. Pat; No. 3,181,442, granted to J. H. Brigel.
  • the present invention overcomes the above noted structural shortcomings and. functional deficiencies of known vibratory compactors by providing a vehicle mounted compactor ofsimplified design that is characterized by a rigid, parallelogram frame for supporting the vibrating elements, such frame being vertically adjustable within guides defined on the vehicle. Consequently, the vibrating elements can be elevated to pass freely over obstacles in the roadbed as the compactor is driven to the work site, and the vibrating elements can be lowered upon reaching the site. Additionally, the amplitude of the stroke of the vibrating elements can easily be varied.
  • the pair of vibrating elements which may be plates, beam, shoes or rollers, are sup ported by the parallelogram frame for both pivotal and vertical movement.
  • the driving means for imparting vibratory energy to the vibrating elements can be provided over a wide range of frequencies, thereby enabling the compactor to satisfactorily compress a wide variety of materials.
  • Vibration dampeners deaden harmful, reactive forces and extend the useful life of the instant vibratory compactor.
  • sundry combinations of springs are utilized to establish a desired natural, or inherent, frequency for the frame.
  • a vibration generator is positioned directly on each vibrating element, so that the driving mechanism is far simpler in design than the conventional complex power take-off belt arrangement utilized for sequentially driving each vibrating shoe in the multi-shoe compactors described above.
  • the driving mechanism includes two cranks operating 180 out of phase so that one vibrating element is engaged with the material to be compacted while the other vibrating element is raised to its highest point of travel.
  • the pneumatic circuits may include various combinations of pistons, manually adjustable pressure limiting valves, pneumatic reservoirs or accumulators.
  • the vibrating elements per se, may be assembled from simplified, hollow components.
  • the vibrating elements may thus be readily altered in size, and their light weight reduces the magnitude of their inertial forces.
  • Sheepsfoot protuberances may be formed on the compacting surface.
  • conventional vibrating shoes were heavy unitary members that lacked versatility in size and shape.
  • FIG. 1 is a side elevational view of a vehicle mounted vibratory compactor constructed in accordance with the principles of the instant invention
  • FIG. 2 is a horizontal cross-sectional view of the vibratory compactor, such view being taken along line II-II in FIG. 1 and in the direction indicated;
  • FIG. 3 is a vertical cross-sectional view of the vibratory compactor with the vibrating elements in the elevated position, such view being taken along line IIIIII in FIG. 1 and in the direction indicated;
  • FIG. 4 is a vertical cross-sectional view identical to the view of FIG. 3, but showing the vibrating elements in a lowered position;
  • FIG. 5 is a side elevational view, on an enlarged scale, of a preferred embodiment of the frame for supporting the vibrating elements
  • FIG. 6 is a side elevational view of a modification of the vibratory compactor of FIGS. 1-5, such view showing additional tools mounted on the vehicle frame;
  • FIG. 7 is a combined side elevational view and schematic representation, on an enlarged scale, of a first alternative embodiment of the frame for supporting the vibrating elements and the drive mechanism for imparting vibratory energy thereto;
  • FIG. 8 is a horizontal cross-sectional view of the first alternative embodiment of the frame for supporting the vibrating elements, such view being taken along line VIII-XIII in FIG. 7 and in the direction indicated;
  • FIG. 9 is a graphical representation of the cycle of operation for the frame and vibrating elements shown in FIGS. 7 and 8;
  • FIGS. 10 and 11 are side and front elevational views, respectively, of the drive mechanism for imparting vibratory energy to one of the vibrating elements of the embodiments of FIGS. 15, 6, or 7-8;
  • FIG. 12 is a schematic representation of an alternative drive mechanism for imparting vibratory energy to one of the vibrating elements of the embodiments of FIGS. 1-5, 6 or 7-8;
  • FIG. 13 is a combined side elevational view and schematic representation, on an enlarged scale, of a second alternative embodiment of the frame and the drive mechanism for imparting vibratory energy thereto;
  • FIG. 14 is a vertical cross-sectional view of the embodiment of FIG. 13, such view being taken along line XIVXIV and in the direction indicated;
  • FIGS. l5l9 are schematic representations of various mechanical spring systems, including appropriate guides, for imparting vibratory energy to the vibrating elements;
  • FIGS. and 21 are side and front elevational views, respectively, of another mechanical spring system for imparting vibratory energy to the vibrating elements;
  • FIGS. 22-25 are schematic views of pneumatic systems for imparting vibratory energy to the vibrating elements
  • FIGS. 26 and 27 are side and front elevational views, respectively, of an alternative mechanical spring system for imparting vibratory energy to the vibrating elements;
  • FIG. 28 is a schematic view of a mechanical spring and compensating weight system for dampening vibrations
  • FIG. 29 is a detail view of the compensating weight used in the system of FIG. 28.
  • FIGS. 3034 show constructional details of the vibrating elements.
  • FIGS. 15, and the variant shown in FIG. 6, depict a carrier vehicle including a chassis l with two axles 3.
  • Five pneumatic tires 2 are arranged on the axles 3 in an offset fashion so that the displaced tracks exert a compacting pressure upon the surface of the road or upon the material to be compacted.
  • the carrier vehicle can be propelled forwards and backwards at variable speeds; and can be steered with great facility.
  • Frame 5 may be supported for movement within the guides by rollers or guides, and the frame may be moved vertically by various conventional devices, such as worm gears, hydraulic actuators, etc.
  • the vibrating elements consist of a pair of vibrating plates, although vibrating beams, shoes, or rollers can be substituted therefor.
  • FIG. 5 The constructional details of the frame 5 which supports the pair of vibrating elements 6 are best shown in FIG. 5.
  • the vibrating elements are held parallel to one another by a pair of horizontally extending control arms 7; the upper control arm is secured to the end plate 8 by a pin or shaft 9, while the lower control arm is secured to plate 8 by a pin or shaft 10.
  • the ends of the control arms 7 furthest from shafts 9 and 10 are secured to side supports 13 by bolts or shaft 14, 14' and corresponding slots which function as hinges for the parallelogram frame 5 and permit a slight rocking movement of the vibrating elements in response to the vibration generators.
  • the midpoints of control arms 7 pivot about shafts 9 and 10, which are situated in the same vertical plane passing through the center of plate 8. Roller bearings may be positioned about shafts 9, 10 to facilitate movement of the arms about the shafts.
  • the braces further enhance the strength of the frame supporting the vibrating elements.
  • the optimum location for the total center of mass for the means for imparting vibratory energy to vibrating elements 6 is located in the vertical plane defined by shafts 9 and 10.
  • the equilibrium position for parallelogram frame 5 is shown in FIG. 5.
  • the shafts 14 are situated a short vertical distance above shaft 10, and shafts 14' are situated a short vertical distance above shaft 9. Accordingly, when one of the vibrating elements is lowered to its operative position, the frame will exert an unbalancing force with respect to the lowered element.
  • Vibration generators 15 of conventional design are secured directly upon compacting elements 6, as shown in FIG. 5.
  • the main engine (not shown) for the compactor which may be an internal combustion engine, transmits power to the generators over a system of transmission belts, including belt 21, which is entrained over pulley 20 on shaft 19, and horizontally extending power take-off belts 30, which are also entrained over pulleys l7 and 20.
  • Shaft 19 extends laterally between cover plates 8 of frame 5, and is situated vertically intermediate shafts 9 and 10.
  • the right hand vibration generator operates out of phase with the the left hand vibration generator. Accordingly, the vibrating '5 elements 6 will always be moving in opposite vertical directions; by virtue of the configuration of frame 5, the vibrating elements will also always be pivoting or oscillating about shafts 9, in opposite directions.
  • vehicle 1 is driven to the work site with frame 5 and compacting elements 6 in the elevated position shownin FIG. 3.
  • the frame and the compacting elements will be lowered into the position shown in FIG. 4.
  • the elements 6 will press against the ground and be vibrated by vibration generators 15.
  • Frame 5 can be vertically adjusted within guides 4 to accurately vary the amplitude, or length of travel to an extreme up or down position from a mean position of vibrating elements 6.
  • the oscillating frequency of the vibrating elements is adjustable by altering the rotational velocity of vibration generators 15.
  • the weight of the vehicle exerted upon the offset pneumatic tires 2 as the vehicle moves to the work site enhances the efficiency of the compactor.
  • the carrier vehicle 1 is provided with oppositely disposed scraper blades 38, 39 and a scarifler 40. Consequently, such embodiment may be utilized as a road working machine of increased versatility for handling bituminous or similar paving materials along a roadway.
  • FIGS. 7-8 shows a frame, indicated generally by reference numeral, 102, and including large plates 102a at opposite sides of the chassis mounted for movement relative to the carrier vehicle 101.
  • Two vibrating elements 103 are secured to each end plate 102and large plate 102a of the frame by shafts 104' which pass through the horizontally extending control arms 104.
  • a crank 106 and a rod 107 are connected to each end of the control arm, and a spring 105 extends between the lower end of rod 107 and vibrating element 103 and opposes the downward movement of the rod.
  • Springs 105 may be spiral springs or torsion springs, and crank 106 and rod 107 are only schematic representations of one type of conventional vibration generator.
  • cranks 106 are driven from the prime mover in a conventional fashion, so that the elements 106 start to vibrate with a phase lag of 180 between one another.
  • the frame and the vibrating elements because they are influenced by springs 105, are a part of an oscillating or vibratory system that has a definite natural frequency.
  • the amplitude of vibrating elements 103 is usually very small but increases sharply when the speed, or frequency, of the crank rotation falls within the resonance range for the springs.
  • crank 106 startsto rotate, at a speed or frequency half, or less, than the natural frequency of the system, then the vibrating elements will be subjected to a forced oscillation of sucha minute amplitude that they will not even completely close the 2 centimeter gap and touch the ground.
  • the frequency of cranks 106 approach the natural frequency of the system, the energy driving forcesimparted by the prime mover to the vibration generators increase in effectiveness.
  • FIG. 9 graphically represents the course of the oscillatory movement of vibrating element 103 during a cycle of operation. Assuming that the movement of element 103 approximates a sinusoidal path of travel and plotting the amplitude of movement versus time, A designates its upper amplitude, A its lower amplitude, and T the period of time for execution of a complete cycle. T is the time interval during which the vibrating element compresses the ground and performs work, T is the interval during which the vibrating element releases its compressive forces and starts its upward movement away from the ground, and T is the interval during which the vibrating element does not touch the ground at all.
  • vibrating element 103 only approximates a sinusoidal function.
  • the variations from the theoretical sinusoidal function are attributable, in part, to the effect of the natural or inherent frequency of springs and the mass of frame 102 and the components suspended therefrom.
  • the movement of the oscillatory system changes rapidly at time T, because of the impact of vibrating element 103 with the ground, and the reaction forces thereby set up in the vibrating element and the frame supporting same.
  • the path of oscillatory movement closely approximates the ideal or theoretical function f, for the companion element 103 only exerts a minimal influence upon the system.
  • the vibrating element accomplishes work compressing the plastic, semiplastic, or hard soil, or other particulate material, while overcoming the initial inertial resistance of the frame to movement.
  • the vibrating element may be assisted in small measure by the resil iency of the material being compacted.
  • the resiliency of the material being compacted becomes an insignificant factor when compared to the amplitude of the vibrating element.
  • the magnitude of the resilient force of the material becomes insignificant by comparison.
  • FIGS. 78 utilizes a single spring 105 at opposite end of each vibrating element
  • the embodiment of FIGS. 10 and 11 utilizes a pair of coil springs 108 in lieu of the single spring.
  • Both springs are situated within cylinder 109 which tapers outwardly at its opposite ends, and the rod 107 is driven by crank 106 and is secured to the upper end of the cylinder.
  • Two diametrically opposite, axially extending sections 110 are removed from the central portion of cylinder 109, and stub shafts extend through open sections 110 and maintain a spacer 111 intermediate the two springs.
  • each stub shaft extends axially through sleeve 112 which concentrically surrounds cylinder 109, while the opposite end of each shaft is mounted for pivotal movement by a journal 116 in bracket 113.
  • the brackets are fastened directly to the upper surface of vibrating element 103.
  • the pair of springs 108 are easily assembled within cylinder 109 in operative relationship in the following manner.
  • the shafts 115 are removed from engagement with brackets 113 and end caps 114 are removed from the opposite enlarged ends of the cylinder.
  • Springs 108 are then inserted into the cylinder, and end caps 114 are then pushed into position, firmly seating the springs. Aligned holes are drilled through the central portion of the first end cap, the spacer Ill and the second end cap. One end of rod 107 is then seated within the hole in the upper end cap.
  • crank 106 Due to the oscillatory movement of crank 106, rod 107 moves vertically and the upper end cap 114 slides within the enlarged upper end of cylinder 109.
  • the cylinder also pivots about stub shafts 115 in response to the movement of rod 107.
  • the movement of the end cap compresses the upper spring 108, and the resultant forces are transmitted through spacer 111 and stub shafts 115 to brackets 113 and thence to vibrating elements 103.
  • the springs are retained in fixed position by annular projections 117 on end caps 114 and annular projections 118 on spacer 111.
  • the cylinder 109 prevents kinking of the springs as they are compressed.
  • the natural frequency of the oscillating system is determined by the combined mass of pivotally mounted cylinders 109 and the springs seated therein.
  • FIG. 12 utilizes a pair of spaced parallel springs 119 in lieu of the springs 105 of the embodiment of FIGS. 7 and 8, or the opposed pairs of prestressed springs 108 of the embodiment of FIGS. -11.
  • the piston rod 107 which is driven by the crank at one end, is secured to a beam 120 at its opposite end.
  • the parallel springs 119 extend between the beam and the vibrating element 103, and beam 120 is movable vertically within guides in frame 102. Both springs act as pressure springs, and together with the other components secured to frame 102, form an oscillatory system. Such system may have the same natural frequency as the oscillating systems of FIGS. 7-9 and 10-11, or it may have a different natural frequency.
  • pressure springs 130 extend through cylinders 130' at opposite ends of vibrating element 103, and pressure spring 131 is connected between plate 132 and the midpoint of element 103.
  • Plate 132 is connected to the lower end of rod 107, which is driven by crank 106.
  • the upper ends of springs 130 rest against ledges 130" on the inner surface of frame 102.
  • Springs 130 and 131 have the same effect upon the natural frequency of the oscillatory system as springs 105 in the embodiment of FIGS. 7-8. Under normal operating conditions, a portion of the reactive forces caused by the vibrations of element 103 striking the ground is transferred through springs 130 directly to the frame 102, while by-passing the vibratory drive mechanism 106, 107, 131 and 132.
  • the ratio of the reactive forces transferred directly to the frame 102 to the reactive forces transferred back to the oscillation drive mechanism is directly proportional to the ratio of the force of springs 130 to that of spring 131.
  • the larger the ratio of the force of springs 130 to that of spring 131 the greater the amount of reactive force transferred directly to the frame 102.
  • the frame obviously, is of sturdy construction and can easily withstand forces of such magnitude while increasing the operational life span of the other components of the oscillating system.
  • the pair of vibrating elements are supported for vertical movement, as well as pivotal movement, by a rigid parallelogram support frame including spaced side supports, a pair of control arms 104, and a pair of spaced shafts 104' about which the control arms can pivot.
  • FIG. 15 is a detailed view of the vertical guide 133 that controls the movement of beam 132, which is connected to the lower end of rod 107.
  • Springs and 131 are also provided with suitable guides, such as cylinders 133, to prevent sidewards kinking during compression thereof.
  • FIG. 16 illustrates another guide adapted to restrain the movement of two, or more, springs.
  • the guide which is indicated generally by reference numeral 133, includes a pair of rods 134 extending upwardly from compacting element 103, and a beam 135 which moves vertically along both rods. Rods 134 extend upwardly through guide surfaces 136 which are secured to the guide 133; the guide, in turn, is secured directly to the frame 102.
  • a first spring 138 is located on each rod between the upper end of compacting element 103 and beam 135; a second spring 139 is located on each rod between beam 135 and guide surface 136; and a third spring 140 is located on each rod between guide surface 136 and enlarged stop 137 atop the rod. All of the springs are prestressed in the position shown in FIG.
  • crank 106 When crank 106 is rotating in a clockwise direction,
  • springs 139 are compressed while springs 138 are relaxed, and vibrating element 103 follows the vertical movement of beam 135 due to the action of springs 140 and guide 133. At the midpoint in the cycle the process is reversed, and springs 138 are compressed while springs 139 are relaxed, so that vibrating element 103 follows the movement of beam 135 against the resistance of springs. 140.
  • the vibrating element 103 oscillates due to the vertical reciprocation of beam 135. When the resonance frequency of the system is reached, the system is damped only by air resistance, internal friction in springs 138, 139 and 140, and by the work done during compacting the ground.
  • FIG. 17 illustrates another guide adapted to restrain the movement of three parallel springs.
  • the guide which is against indicated generally by reference character 33, includes an additional spring 141 that is positioned about a rod 142 secured to the upper surface of element 103.
  • Spring 141 extends between a stop 143 at the upper end of rod 142 and a supporting surface on the cylindrical member 144 that is mounted beneath plate 145.
  • the cylindrical member is concentric with rod 142. Consequently, as plate 145 is vertically reciprocated by crank 106 and rod 107, the movement of cylindrical member 144 compresses, and relates spring 141.
  • guide 233 functions in the same manner as guide 133 in FIG. 16.
  • FIG. 18 depicts another mechanical spring system for effectively transmitting vibratory energy from an internal combustion engine, or other conventional prime mover to the vibration generator, and thence to the vibrating elements 103.
  • a beam 155 is secured across the open upper end of element 103, so that the beam and the interior walls of the element define a chamber 148 therebetween.
  • An aperture is formed in the center of the beam, and a piston rod with an enlarged lower end 149 extends therethrough.
  • a first spring 146 extends between end 149 and the bottom surface of chamber 148.
  • a pair of spaced rods 134 are secured to the upper surface of beam 155, and a pair of guide surfaces 136 extend inwardly from guide 133.
  • a first spring 139 is located on each rod 134 between beam 155 and surface 136, and a second spring 140 is located on each rod 134 between surface 136 and the enlarged stop 137 atop rod 134.
  • crank 106 and lever 107, beam 155, and thus vibrating element 103 is influenced by the compression of springs 146 and 139 while the springs 140 and 147 are relaxed.
  • beam 155 is influenced by the compression of springs 147 and 140 while springs 139 and 146 are relaxed.
  • FIG. 19 shows a variant of the mechanical spring system of FIG. 18 wherein the chamber 148 defined between beam 155 and the internal walls of vibrating element 103 has been enlarged. Also the springs 146, 147 operatively associated with piston rod 150 have been eliminated, rods 134 have been lengthened, and beam 150' is secured to the lower end of rod 150 and moves vertically along rods 134. Springs 160 are tensioned, when springs 161. are relaxed, and vice versa. Springs 160 act in concert with springs 139, while springs 161 act in concert with springs 140. The net result is that energy imparted by crank 106 and rod 107 is effectively transmitted by the springs and beam 150 to parallel beam 155 and vibrating element 103.
  • FIGS. 20 and 21 disclose a mechanical spring system for transmitting a portion of the spring forces directly to the frame supporting elements 103, such as frame 102 shown in the embodiment of FIGS. 7 and 8.
  • Brackets 162 and 163 are secured directly to the heavy plate 102(a) of frame 102.
  • a first spring 164 has one end centered and seated firmly in bracket 162 and the rest of the spring extends downwardly toward bracket 163.
  • a second spring 165 has one end centered and seated firmly in bracket 163, and the rest of the spring extends upwardly toward bracket 162.
  • a bar 166 extends horizontally across the upper end of supports 167, and the lower end of spring 164 and the upper end of spring 165 are centered and seated firmly therein.
  • the lower end of supports 167 is connected to one end of control rod 104. Alternatively, the lower end of the support could be connected directly to vibrating element 103.
  • FIG. 22 shows a pneumatic servo-piston that may be used in combination with mechanical spring systems shown in FIGS. -21, or in lieu thereof.
  • Such pneumatic servopiston may be used as a solitary control device or as an integral part of a pneumatic control circuit.
  • the pneumatic servo-piston includes a cylindrical housing 168 and a piston 169 mounted piston rod 170 so as to movable within the housing.
  • a flrst pressure limiting valve 171 is operatively associated with the mid-section of the housing, while a pair of pressure limiting valves 172 are situated at opposite ends of the housing. Valves 172 limit the maximum pressure built-up within the housing, while valve 171 determines the minimum pressure level within the housing. Consequently, the pneumatic servo-piston operates with a particular volumetric efficiency over a selected range of pressures, and closely approximates the action of a mechanical spring.
  • valves 171 and 172 can be adjusted by varying the settings of valves 171 and 172 so that the power transmitted to compacting elements 103 from crank 106 and rod 107 can be adjusted. Also, the valve settings may be altered to overcome the effects of inertia when starting crank 103 in motion or when attempting to stop same once it is in motion.
  • FIG. 23 shows a pneumatic circuit including the pneumatic servo-piston of FIG. 22 and further including a container 173 of pressurized fluid that is connected through pressure reducing valve 174 to reservoir 175.
  • the pressurized fluid in container 173 influences the movement of piston 169 and piston rod through valves 171 and 172.
  • the servo-piston operated independently of ambient air conditions and pressure changes. Additionally, the valves may be adjusted so that the servo-piston may be adjusted into harmony with the operation of the various mechanical spring systems.
  • FIG. 24 shows another pneumatic servo-piston that can be utilized within the power transmitting system of the instant invention.
  • Such servo-piston includes a cylindrical housing 176 which may be open at both ends, and a middle partition 177 which extends perpendicular to the axial dimension of the cylinder and divides same into two chambers.
  • a pair of pistons 178 are spaced along piston rod 179 at opposite sides of partition 177. The rod passes through an aperture in the center of partition 177, and the pistons move along the inner wall of housing 176.
  • FIG. 25 shows a pneumatic circuit including the pneumatic servo-piston of FIG. 24 and further including a container 191 of pressurized fluid that is connected through pressure reducing valve 184 to reservoir 195.
  • the chamber formed above partition 177 is connected to container 191 via conduit and adjustable valve 192, while the chamber formed below partition 177 is connected to container 191 via conduit and adjustable valve 193.
  • An equilibrium condition occurs during the operation of pistons 178 and piston rod 179 wherein the fluid entering housing 176 from container 191 on each piston rod stroke is equal to the fluid leaving. housing 176 and returning to container 191.
  • Such condition is related to the volumetric effeciency of the servo-piston, and influences the power transmitted to compacting element 103.
  • the equilibrium condition can be altered by varying the settings of valves 192, 193 and 194.
  • crank 106 and rod 107 can be stopped even through crank 106 and rod 107 are running by the simple expedient of venting valves 192, 193, to relieve any pressure build-up.
  • crank 106 and rod 107 can be brought up to full speed before connecting housing to the source 191 of pressurizedfluid. In both instances, the crank can not transmit power to the vibrating elements.
  • valves 192, 193 are adjusted accordingly.
  • an adjustable valve 196 or a variable stop member, or the like, is positioned within conduit 197 which communicates with opposite sides of partition 177.
  • Valve or stop 196 can readily be adjusted, and valves 192, 193 can be set once and such setting can be maintained constant, if so desired.
  • FIGS. 26 and 27 show a combined pneumatic servopiston and spring system for transmitting energy to compacting element 103.
  • the servo-piston includes a

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  • Agronomy & Crop Science (AREA)
  • Environmental & Geological Engineering (AREA)
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US00178567A 1970-09-23 1971-09-08 Vehicle mounted vibratory compactor Expired - Lifetime US3834827A (en)

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US504560A US3923412A (en) 1970-09-23 1974-09-09 Drive means for vehicle mounted vibratory compactor

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DE19702046840 DE2046840A1 (de) 1970-03-04 1970-09-23 Vorrichtung zum Verdichten von Bodenschichten

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3909148A (en) * 1972-06-24 1975-09-30 Koehring Gmbh Bomag Division Vibratory compacting machine
US4607980A (en) * 1984-12-06 1986-08-26 Spetsialnoe Konstruktorskoe Bjuro "Stroimekhanizatsia" Apparatus for compacting soil, concrete and like materials
US6213681B1 (en) * 1997-07-23 2001-04-10 Wacker-Werke Gmbh & Co., Kg Soil compacting device with adjustable vibration properties
RU2254410C1 (ru) * 2004-06-24 2005-06-20 Бычков Аркадий Иванович Устройство для уплотнения грунтов
USD889762S1 (en) * 2019-01-18 2020-07-07 James A. Taylor Compactor buggy

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US2254744A (en) * 1939-08-11 1941-09-02 Jackson Corwill Tamping machine or apparatus
FR1125862A (fr) * 1955-06-08 1956-11-09 Machine routière à déplacement continu pour le damage des matériaux formant la route
GB824948A (en) * 1956-05-29 1959-12-09 Koehring Co Segmented roll and compaction method
GB897636A (en) * 1957-09-12 1962-05-30 Warsop Power Tools Improvements in apparatus for tamping soil and the like
AT225222B (de) * 1959-01-16 1963-01-10 Losenhausenwerk Duesseldorfer Verfahren und Vorrichtung zur Bodenverdichtung mittels Rüttelschwingungen
US3260177A (en) * 1964-02-24 1966-07-12 Rex Chainbelt Inc Laying reinforced concrete pavement
US3283677A (en) * 1964-09-01 1966-11-08 Wacker Hermann Manually guided motor driven tamping device for earth, concrete and other materials
US3369459A (en) * 1965-01-04 1968-02-20 Earl H. Fisher Hydraulic intake and exhaust valving arrangement
DE1262913B (de) * 1959-10-15 1968-03-07 Losenhausen Maschb Ag Bodenverdichter
US3577897A (en) * 1968-11-12 1971-05-11 Albert G Bodine Sonic method and apparatus for laying and repairing asphalt material

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US1265499A (en) * 1917-08-01 1918-05-07 Alan Jay Parrish Machine for making concrete pavements and the like.
US1538527A (en) * 1922-05-08 1925-05-19 Murphy John Road tamper
DE629960C (de) * 1929-04-21 1936-05-16 Karl Witte Stampfvorrichtung mit zwei in der Bewegungsrichtung hintereinanderliegenden, abwechselnd heb- und senkbaren Stampfeinheiten
US2160462A (en) * 1934-12-07 1939-05-30 Schieferstein Georg Heinrich Ramming machine
US2254744A (en) * 1939-08-11 1941-09-02 Jackson Corwill Tamping machine or apparatus
FR1125862A (fr) * 1955-06-08 1956-11-09 Machine routière à déplacement continu pour le damage des matériaux formant la route
GB824948A (en) * 1956-05-29 1959-12-09 Koehring Co Segmented roll and compaction method
GB897636A (en) * 1957-09-12 1962-05-30 Warsop Power Tools Improvements in apparatus for tamping soil and the like
AT225222B (de) * 1959-01-16 1963-01-10 Losenhausenwerk Duesseldorfer Verfahren und Vorrichtung zur Bodenverdichtung mittels Rüttelschwingungen
DE1262913B (de) * 1959-10-15 1968-03-07 Losenhausen Maschb Ag Bodenverdichter
US3260177A (en) * 1964-02-24 1966-07-12 Rex Chainbelt Inc Laying reinforced concrete pavement
US3283677A (en) * 1964-09-01 1966-11-08 Wacker Hermann Manually guided motor driven tamping device for earth, concrete and other materials
US3369459A (en) * 1965-01-04 1968-02-20 Earl H. Fisher Hydraulic intake and exhaust valving arrangement
US3577897A (en) * 1968-11-12 1971-05-11 Albert G Bodine Sonic method and apparatus for laying and repairing asphalt material

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Publication number Priority date Publication date Assignee Title
US3909148A (en) * 1972-06-24 1975-09-30 Koehring Gmbh Bomag Division Vibratory compacting machine
US4607980A (en) * 1984-12-06 1986-08-26 Spetsialnoe Konstruktorskoe Bjuro "Stroimekhanizatsia" Apparatus for compacting soil, concrete and like materials
US6213681B1 (en) * 1997-07-23 2001-04-10 Wacker-Werke Gmbh & Co., Kg Soil compacting device with adjustable vibration properties
RU2254410C1 (ru) * 2004-06-24 2005-06-20 Бычков Аркадий Иванович Устройство для уплотнения грунтов
USD889762S1 (en) * 2019-01-18 2020-07-07 James A. Taylor Compactor buggy

Also Published As

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