CA1139975A - Mobile apparatus for reverberating surfaces - Google Patents
Mobile apparatus for reverberating surfacesInfo
- Publication number
- CA1139975A CA1139975A CA000297367A CA297367A CA1139975A CA 1139975 A CA1139975 A CA 1139975A CA 000297367 A CA000297367 A CA 000297367A CA 297367 A CA297367 A CA 297367A CA 1139975 A CA1139975 A CA 1139975A
- Authority
- CA
- Canada
- Prior art keywords
- hammers
- rack
- frame
- bank
- carriage
- Prior art date
- 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
Links
Classifications
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- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
- E01C23/00—Auxiliary devices or arrangements for constructing, repairing, reconditioning, or taking-up road or like surfaces
- E01C23/06—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road
- E01C23/09—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road for forming cuts, grooves, or recesses, e.g. for making joints or channels for markings, for cutting-out sections to be removed; for cleaning, treating, or filling cuts, grooves, recesses, or fissures; for trimming paving edges
- E01C23/0906—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road for forming cuts, grooves, or recesses, e.g. for making joints or channels for markings, for cutting-out sections to be removed; for cleaning, treating, or filling cuts, grooves, recesses, or fissures; for trimming paving edges for forming, opening-out, cleaning, drying or heating cuts, grooves, recesses or, excluding forming, cracks, e.g. cleaning by sand-blasting or air-jet ; for trimming paving edges
- E01C23/0926—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road for forming cuts, grooves, or recesses, e.g. for making joints or channels for markings, for cutting-out sections to be removed; for cleaning, treating, or filling cuts, grooves, recesses, or fissures; for trimming paving edges for forming, opening-out, cleaning, drying or heating cuts, grooves, recesses or, excluding forming, cracks, e.g. cleaning by sand-blasting or air-jet ; for trimming paving edges with power-driven tools, e.g. vibrated, percussive cutters
-
- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
- E01C23/00—Auxiliary devices or arrangements for constructing, repairing, reconditioning, or taking-up road or like surfaces
- E01C23/06—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road
- E01C23/08—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road for roughening or patterning; for removing the surface down to a predetermined depth high spots or material bonded to the surface, e.g. markings; for maintaining earth roads, clay courts or like surfaces by means of surface working tools, e.g. scarifiers, levelling blades
- E01C23/085—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road for roughening or patterning; for removing the surface down to a predetermined depth high spots or material bonded to the surface, e.g. markings; for maintaining earth roads, clay courts or like surfaces by means of surface working tools, e.g. scarifiers, levelling blades using power-driven tools, e.g. vibratory tools
- E01C23/0855—Devices or arrangements for working the finished surface; Devices for repairing or reconditioning the surface of damaged paving; Recycling in place or on the road for roughening or patterning; for removing the surface down to a predetermined depth high spots or material bonded to the surface, e.g. markings; for maintaining earth roads, clay courts or like surfaces by means of surface working tools, e.g. scarifiers, levelling blades using power-driven tools, e.g. vibratory tools moved rectilinearly, e.g. scabblers
Landscapes
- Engineering & Computer Science (AREA)
- Mining & Mineral Resources (AREA)
- Architecture (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Mechanical Engineering (AREA)
- Road Repair (AREA)
Abstract
ABSTRACT OF THE INVENTION
A ceramic fiber and a shrink resistant article manufactured therefrom. The fiber comprises at least 80 weight percent of a refractory compound selected from the group consisting of silica, alumina, aluminum silicate, titania, zirconia, zirconium silicate and mixtures thereof and which comprises less than 5 combined weight percent of alkali or alkaline metal oxide or alkali or alkaline metal silicate. The fiber is uniformly coated with from about 0.01 to about 5 weight percent of Cr2O3.
A ceramic fiber and a shrink resistant article manufactured therefrom. The fiber comprises at least 80 weight percent of a refractory compound selected from the group consisting of silica, alumina, aluminum silicate, titania, zirconia, zirconium silicate and mixtures thereof and which comprises less than 5 combined weight percent of alkali or alkaline metal oxide or alkali or alkaline metal silicate. The fiber is uniformly coated with from about 0.01 to about 5 weight percent of Cr2O3.
Description
TI TLE
.
MOBILE APPARATUS FOR REVERBERATI~G
SURFACE S
INVENTOR
Ronald A . W . CLARKE
ABSTRA(::T OF THE DISCLOSURE
. . . _ A mobile impacting device which is self propelled at controlled speeds has a plurality of independently con-trollable hammers which drive percussion tools into impacting blows with the surface to thereby erode the surface and or cut grooves and or cut holes. By the relative control of the speed of travel of the device the number of hammers actually impacting ~he surface and the position of the hammers erroding the surface, cutting grooves into the surface, or hole cutting can be achieved.
By the particular cantilever coniguration of the hammers relative to ~he contact running wheels of a mobile device, the device can accom~odate erosion groove cutting pr hole cu*ting in confined areas. In fact it also has the advantage in bump cutting, that is the elimination of surface disconti-uity.
.
., This invention relates to a mobile apparatus for reverberating surfaces.
More recently, it has become known that if a rigid surface is struck rapidly with a series of impact blows, the surface impacted and its substrate, are stressed, during impact into compression and during thè interval between stikes (impacts) the substrate and surface reElex into tension. Some materials for example concrete or rock reflex better under compression than tension; thus the series of impact blows to the concrete surface will erode the surface away but will not injure ~he substrate. The absence of damage to the underlying structure and substrate, is due to the fact that when each impact tool strikes the surfa~e, it causes the material within its area to deflect, thereby creating a momentary and localized compression of the material. The compressive strain of the material is mainly elastic and therefore almost immediately given up in generating a rebound in the material thereby causing the material to pass through its relaxed state into one of tension nearIy equal to the initial compression. As the material is much weaker in tension than compression, it is unable to a~hieve the level of tensile strain corresponding to the previous compressive strain. The material consequently fractures, the elastic energy being given up as kinetic energy and fragments thrown out of the s~rface o~
the material. This percussive action takes place with great rapidity. This allows for the treatment of concrete surfaces for removal of surface laitances or imbedded contaminants such as rubber which if severe enough will render the surface slick reducing the inherently acceptable level of the static coefficient of friction for the surface. This is undesirable when the surface is a heavily travelled one such as an airport runway or motorways (highways) since the reduction in the coefficient of friction for the surface reduces traction of tires and hence safety tolerances.
It is also known that certain concrete motorways or runways and in particular bridge deckings, such as those carrying motorway surfaces tend to disintegrate most notably as a result of the combiried influences oE freezing and thawing cycles, moisture and salt. These conditions are typically encountered in the temperate regions of the globe and are notable in environments similar to Ontario, ~anada where the yearly freezing and thawing cycles extend over many months commencing in mid October and extending through the winter into early or mid April and sometimes ZO even May. W~th moisture converting to ice, and binding itself to the insites of the concrete surface, concrete surface breakdown is inevitable. This ~reakdown is even encouraged when calcium chloride is used, by road crews, to melt the ice so that the road surface~ will turn into a wet but not an icy state, a more desirable condition for travelling of vehichles.
Thus, regions in such surface which have disintegrated must be removed prior to restoration.
Typically this has been done by jack hammers~
When in England, I developed a stationery device which provides a rack with reciprocating hammers/ and percussion tools, which impact the surface over a sufficient elapsed time to cut holes of controlled shape and depth into concrete. 'm e percussion tools are travelled in relative orthoginal direction in a frame of the stationery device in order to impact over a control region. It was ~hen an easy matter to remove the debris (detritus) from the hole, coat the hole with a bonding agent, and insert a preformed or precast slab into the hole - the repairs were performed in unprecidented time.
~ owever, on reflection, this technique is inadequate, not because controlled impacting does not per~orm controlled cutting well, but rather on the contrary~
Controlled cutting is performed so well as to shape of aperture and its depth, that my earlier stationery device performed the cutting task archaically and wholly inadequately because it had to be manhandled from operational site to operational site, when site changes where desired; further in operation the de~ice had to be mounted or~affixed to the road surface prior to use.
I then conceived of a mobile device with impacting hammers mounted between fore steerable wheels and rear driver wheels.
I have now conceived of a device which is self-propelled at controlled speed and has a plurality of independently controllable hammers which drive percussion tools into impacting blows with the surface; that is into the surface subadjacent to each tool. By relative ~ontrol of both speed of travel of the device, zero to a maximum, and the number of hammers impacting the surface, on the one hand~ larger surface areas may be stripped of surface laitances; or, on the other hand, controlled shapes of apertures and of depths may be cut into the surface or substrate as desiredO By cantilever configuration of the hammers, relative to the surface contact running wheels of the devlce, the device travels the percussion tools over the surface to be treated in advance of the contact runnin~
wheels. Further benefits are thus achieved. Firstlyl the a~ility to impact the surface in confined reyions as commonly found at corners of a surface which mate to adjoining uprising walls and secondly the ability to smooth out surface discontinuities ("bump cuttingl') as is commonly found between sheets of adjoinin~ surfaces which have experienced localized settling or heaving.
The invention also achieves a device which may cut holes into the surface of predetermined shape, size and depth.
Further-the invention achieves means for erroding surfaces by an essentially "dry process" and for facilitating the collection of detritus and thus eliminates any ~lurry that would otherwise be caused by the use of large amounts of waters necessary to flush away the detrikus. Wetting the impact surface is thus avQided as a wet state surfa~e causes slower cutting and erroding than on a dry surface. Thus the region above the surface of impact is to be treated with a vapour mi5t and preferably a sweeper sweeps the treated area thereafter.
Further collection of detritus is enhanced with a sweeper and a vacuum collection device which are integral to the device (vacuum eleaner).
The invention therefore contemplates a mobile apparatus for imparting percusive blows to an underyling surface over whieh the apparatus may travel comprising:
(a) carriage means having axles with running wheels engaging the surface by which the carriage may be travelled thereon;
(b) a plurality of adjacently disposed hammers mounted in a bank with percussive tools, depending from the hammers, located intermediate the bank and the underlying surface, the hammers responsive to a flow of eurrent through the hammer by which the hammer is activated to reciprocate the percussive tool into periodie contact with the surfaee~ and, (c) means for mounting said bank along one peripheral edge of the carriage means.
The invention will now be clescribed by way of example and reference to the accompanying drawings in whieh:
Figure 1 is a side elevation of an embodiment.
Figure 2 is a side eleYation of an alternative embodiment employing a rotary sweeper for removing debris.
~igure 3 is a seetion along III-III of figure 2.
Figurè 4 is a perspective of fore and aft hammer raeks and the means by whieh each of the hammers is relatively positioned.
Figure 5 i.s a perspeetive of the control means by whieh each of the hammers of figure 4 may be positioned.
Figure 6 is a circuit diagram of the eontrol circuit (for a single ore and aft hammer) by which they are aetivated into operational status for reciprocation.
Y~
Figure 7 is a plan view of an embodiment of a hammer rack allowing relative positioning of fore and aft racks~
Figure 8 is a perspective partially in section of the racks adiustment means of figure 7.
Figure 9 is an elevation, partially in section, of the for laterally tracking means of figure 7.
Figure 10 is a representive profile section of a surface grooved by the hammers of figure 7 through 9 when positions Dl and D2 are coincident.
Figure 11 is a plan view of an alternative means for laterally tracking both banks of hammers relative to the frame using pneumatics or hydraulics.
Figure 12 is a partial view in elevation of the racks of figure 11 indicating the full "offset" position when the percussive tools of one bank overlap in part those of the other bank.
Figure 13 is an elevation o~ a segment of the racks oE
figures 11 and 12 showing alternative means by which grooving of the surface may be obtained ~via independent vertical control~, and the grooved section cut into the surface and substrate.
Figure 14 is a side view in elevation of th-e embodiment of figure 2`illustrating the hydraulic circuit for misting.
Refering to figure 1 a mobile impacting vehicle 10 comprises a frame 11 attached to the front and in cantilever relationship to.a following carriage 12, which carries an axle with a pair of fore running wheels 14 and a second axle carrying a single aft running and steera~le wheel 15, which acts as a turnin~ wheel for the vehicle since it is connected by appropriate linkages 15a to a sterring wheel 18 ~L~3~
for driver control. The actual vertical members to which the frame 11 is attached are shown as members 12' and are integral with the carriage 12. A seat 19 is placed on the top of the carriage 12 for the cornfort of the driver and a plurality of controls 20 which operate the two rows of impacting hammers 30 and 31 located in the lower regions of the frame 11 in a manner which will shortly be described;
control 21 governs the forward or rearward direction of drive. The carriage is driven into travel by an airmotor 23 which transmits motion via pulley 22 and drive belt 24 to a pulley, 14a, on one or both of the fore wheels 14.
Control lever 21, by means not clearly shown in the figures, controls the flow of air into the air motor 23 so that the vehicle 10 may move in a forward or rearward direction under variable and controlled speed.
In the embodiment of figure 1, frame 11 carries two banks of hammers 30 and 31 a single rack 32, so that the hammers are positioned along or across the front pheriphial edge of the vehicle. Each hammer 30, 31 is suspended from the rack 32 to depend downward and expose its hammer shaft 36 on which is carried an cylindrical impacting or compression tool 34 at the end thereof. The tool has a diameter of about 5-6.5 cm. Each hammer 30 or 31 communicates by its own pneumatic conduit 38 to either fore or aft manifolds 39. Each manifold communicates through an interconnecting~manifold conduit 42, to a feed pipe 44, which is connected to an outboard source of pneumatic pressure such as that commonly available from a portable air compressor (now shown). The air compressor (not shown) may be conveniently pulled from a hitch 50 affixed to the rear 3~
of the vehicle lO. In the embodiment of figure l the rack 11 is integral the frame ll which is bolted onto the front pheriphial edge of the carriage 12 as shown. Thus, it is fixedly positioned outboard and in advance of the running wheels 14, hence, in cantilever fashion. The ~hammer) rack 32, on the other hand, may be fixed relative the frame ll but is preferred to be ree to travel ~p and down opposing internal margins of the vertical end members 13 from which the frame is fabricated. This allows the rack 32 and the hammers to be positioned when in operational use into that position shown in figure l; when not in operational use into that position shown partially in phantom. Guide wheels 17 are provided at the upper margins of the rack 32 to guide the rack up and down the opposite facing vertical members 13. The rack 32 is moved up and down under pneumatic and/or hydraulic control by means of a piston cylinder 37 and its moveable piston rod 39; the rod 39 connectin~ to the upper face of the rack 32 through a pivot connection and the cylinder 37 attached to an upper cross member 16 of the frame ll. ~or stability during operation the rack rests on fore and aft lower horizontal end members 29.
Typically, in operation, compressed air is provided to the feed pipe 44 and distributed by the manifold conduit 42 into the fore and aft manifolds 39; thence, into the individual pneumatic conduits 38 to each individual fore hammer 30 and each individual aft hammer 31. The means by which the pneumatic hammers are activated thereby may be conventional; or, as disclosed in my co-pending Canadian Patent ~pplication, Serial No. 273,457, filed ~ March, 1977, g _ 7~
entitled 'Method and Apparatus for Removal of Contaminenets from Surfaces of Materials'. In general, any other means for driving the impactiny tools into reciprocation may be used~ for example electric current operating reciprocating hammers or hydraulics.
I prefer that the mean distance PD between fore running wheels 14 and the region between fore and aEt hammers (mean impact region 53) to be as short as possible say about 7-12 inches (17cm - 30cm~. This will allow positioning of the impact region 53 into corners with ease with the only possible untreatable area being the region in advance of the impact region and behind the front vertical member 13.
In another embodiment, referring to figures 7 through 9, the rack 32 may be provided with a longitudinal slot 33 extending essentially the width of the rack 32 and with an overlaying movable hammer carrying plate 35. The aft hammers 31 then project through the slot 33 but are attached to the overlaying hammer carrying plate 35. To this plate 3~ is attached, at one end a threaded bearing 47~ Through the bearing 47 extends a threaded shaft 46 which also extends through an uprising threaded anchor plate 48 attachèd to the rack 320 The threaded shaft 46 terminates at a hand crank 49 located at its other end~ By rotating the hand crank 49 the relative position of the aft hammers 31 to the fore hammers 30 is changed. In this way the centers of the fore and aft hammers may be deviated under adjustment by the dimension indicated as D in figure 7; that is, from position D~ to Dl. When the aft hammers 31 are located with centers at D2 as shown there is a relative overlap (OL) of each percussive tool 34 depending from the aft bank of hammers 31 relative those of the fore bank 30~
The overlap can be controlled or eliminated by turning the crank whereupon the centers of the aft bank oE hammers 31 are moved from D2 (the overlap position of the percussive tools) into position Dl (the registry position of fore and aft hammers). In the former position D2 the fore and aft running wheels 14 and the region between fore and aft hammers 30, 31 are not irl registry; they impact different underlying surface regions during surface transverse of the underlying surface~ Thus there is i~pact to the total underlying surface.
By altering the relative position of the aft hammers relative the fore hammers, the centers of the fore and aft hammers may be placed in registry~ eg. along line Dl, In ~his way the centers of the fore and aft hammers will be in registry and when the vehicle 10 moves forward the tools 34 of each bank will impact the same surface; gouging and grooving of the surface will result as per figure 10. The ~0 depth of each groove will depend on the speed of traYel and the number of blows impacted to the surface. The grooYe width is ~20L whilè the step is ~-20L where ~ ~s the diameter of the tool 34. Needless to say, with different relative positions of ~he centers of fore and aft hammers the profile of the grooves may be altered.
Referring,now to yet a further embodiment and to figure 2, the mobile vehicle 10 is almost identical to that of figure 1 save in the following respects. Note between the fore wheels 14 and rear wheel 15 is a rotary broom 52 driven by belt 53 via the same pulley 22 from the airmotor 23. It could as conveniently be driven by an inde~endent power source ~not shown~. Further a vacuum cleaner 55 is mounted on top of a water tank 60~ The vacuum cleaner 55 communicates to a collection shute 54 mounted aft of the rotary broom 52~ Driven by conventional means ~not shown) the vacuum cleaner 55 removes via the shute 54 detritus dislodged from the surface as a result of the percussive tool action and the rotary sweeper.
Alternatively, while not confined to the embodiments disclosed in Figures 2 and 3, the frame 11 and its racks of hammers may be fabricated with still additional featuresO
The frame 11 may be adapted for vertical movement relative to the carriage 12. As such, each rear vertical member 13 extends, as shown in s~ction in figure 3, into a I ~male grooved track 113, while the front vertical carriage arm 12 extends into a complimentary mating male runner 112.
As such, the Erame 11 may be movled into its operational position as shown in Fig. 2 or into its rest po ition for travel, as shown in the phantom position 96, for travelling between operational sites. The hammers 30 and 31, en mass are thus lifted ~rom operational to non-operational status.
The means o~ lifting may be accomplished by convenien$ mean~
for example a lift mechanism 95 includes a cylinder 90 whose bottom is affixed to a horizontal cross member 12N
interconnecting the lower termini of the verticàl uprising members 12'. The cylinder 90 has a pusher rod 91, the free end of which carries a parallel gear train 92. Two chains 93 are each attached, at cne end, onto the carriage 12, and threaded over the parallel gear train 92 and terminate at dead soldiers 94 intergal with the vertical members 13. As the cylinder extends the piston 91, the gear train 92 moves upward, and the whole frame 11 is moved to its upper most position 96 shown in phantom.
In yet an alternative embodiment, the hammers and racks may be of different configuration.
Firstly, the single rack 30 can ~e eliminated in favour of a dual rack cage, a fore rack cage 130 and an aft rack cage 231. Each cage has its own rack floor, respectively 13Z and 232; front and rear walls, 133, 133'; 233, 233~; and upper covers 134, 234 which terminate at bushings. These bushings are respectively carried by fore and aft cage support bars 135 and 235 carried by ~not accurately shown~
an upper transverse member T. Tbis completes cage suspension within the frame 11.
Each fore hammer 30 is operationally positioned into the rack plate 132 by its o~n positioning device; namely a pneumatically positioning cylinder and piston assembly 60;
similarly aft hammers 31 into the aft rack plate 232 by penumatic assemblies 61.
2n Referring now to figures 2, 4, 5 and 6, the position o~
each hammer, fore and ~ft, in their respective racks, i5 controlled by a control bar CB, which extends across the lower front face of the frame 11. A plurality of levers 1, or 0 indicating fore or aft racks, and (a through k indicating linear position along each rack) independently actuate each c~inder 60 or 61 into rest or operational status for the respective hammer. Thus, referring to figure 4, hammers 30e through 30k and 31d through 31k are shown at rest while 30a through 30d and 31a throuyh 31c in operational status.
The circuit diagram of figure 6 is representative of the communication by which the hammer is positionally located at rest or in operational status. Namely, from the manifolds 39 a direct feed ta each hammer 30 or 31 is achieved by its own pneumatic conduit 38 as earlier disclosed. The feed' may be add'itionally turned on by an appropriate stop cock or the like ST located in the line~
An auxiallary feed AF communicates with the fore manifold 39 and is the central feed to the control box CB.
Each piston 60 has its own activating conduit fi4 and inactivating conduit 66 which is connected to its own pneumatic switch lever 1 wbich has a common communication~
now shown, via the control Box CE~ to the auxiallary feed A~. The actual lever 1 will be one of la through lk depending upon the positional location of the hammer in the rack~ The activated or non-activated status of each hammer is thus governed by the upward or downward postion of the lever 1. Similarily, for the rear hammers 31 and their assemblies 61 the same are controlled via the conduits 65 and 67 and the appropriate position of levers 0 for each positional location a through k, ~ urther each of the fore and aft cages may be oscillated relative to each other and to the frame 11. Thus each cage has its own oscillitory means; namely, a cylinder 70 with moveable rod 71, the free end of which ~72~ connects to a thrust pl~te extension 73 integrally attached to the cage. The cage itself slides, in response to actuation of the rod, along its own support bar 135 or 235 as the case might be, with the aid of the cage bushings. The cylinder and rod of course may be pneumatic, hydraulic or otherwise.
These embodiments are ideally suited for erroding the total surface area underneath the main frame or alternatively cutting holes or grooves~
In order to facilitate cleaning oE the treated area, by the vertical 10 and referring to figure 2, the vehicle 10 is fitted with a rotary broom 52 of conventional style mounted between the front and rear wheels 14 and 15. The rotary broom is activated of course by its own pulley 53 communicating as well to the air motor 23 and its drive pulley 22. The debris which the broom sweeps up off the treated surface is collected by shute 54 connected to a vacuum device 55 of conventional style, Thus the detritus is accumulated in the vacuum cleaner box 55. In order to reduce the amount of free flying dust and detritus imparted into the atmosphere with each stroke of the impact tool 34, and referring to figures 2 and 14, there is a hydraulic misting circuit comprising a transverse bar 65 mounted between fore and aft hammers with a plurality of spacily disposed misting nozels 67 depending therefrom. The transverse bar 65 communicates by conduit, shown, to a tank reservoir 60 holding water. Air from the manifold 35 is injected into the water reservoir 60 and thereby causes it to be pressurized thereby conveying the water out of the misting nosels 67 to create a mist M in that region and in the space just above the strike region 53. The mist captivates free-dust and flying detritus resulting in a cleaner operation while at the same time leaving the strike surface (hammer lane) dry.
When tool surface area under the frame 11 (hammer lane) is to be treated, fore and aft hammers are positioned in ~ 15 offset as shown in figure 12, so that the peripheral edge of the tandum hammers overlap the adjacent hammer of the other rack or cage. The perferred overlap, OL, is about 2mm when the tool head diameter is about 5 - 6.5 cm.
When the holes are to be cut, for example H of figure 4, this may be achieved as follows. ~ammers 30a through 30d r and at hammers 31a through 31c are placed in the activated status. The hole as shown will be cut. This requires that both fore and aft racks 32 and 232 must be oscillated relative the rame ~if both racks are to be used as shown). The oscillation of the racks to registers and unregisters the centers of each of the fore and aft cut-ting hammers. Expressing this another way, it is necessary to reduce the dimension D as seen in figure 7, from 0 to its maximum displacement and back again. (The manual operation of this facility, as earlier described in reference to the embodiment of figures 7, 8 and 9 is cumbersome)~ Hence, I
prefer referring to the embodiments of figure ll, to oscillate both racks. There the aft hammers 30 are driven to and fro as are the fore hammers under the control of their own reciprocating cylinders 70, and rods 71 which connected to their thrust plate extensions 73 integrally attached to either the fore cage 130 or rea~ cage. In this manner the cages are driven, relative to the frame back and forth as generally indicated by the arrows in figure 4.
The shape of the hole H is cut as shown; the depth of the hole is governed by the duration of and extend of the impact blows.
A slower but acceptable method of cutting a hole H
3~ would be to deactivate all fore hammers 30 and to have but a single reciprocating cylinder 70, rod 71, rod head 72, connecting to a single thrust plate extension 73 integrally attached to the single cage eg. cage 231. The fore cage 130 would be fixed and not capable of oscillation. The f~re hammers would be placed into the inactive position~
The rear hammers 31 a, b and c, would be activated and the rear rack oscillated, while the truck lQ removed firstly forward and then rearward so as to cut the hole to its.
desired length; the depth of the hole of course would be controlled by the number of passes forward and backward of the hammers and of course the rapidity of the strike and the strength strike impact blow. Typically with air pressures on the pneumatic hammers ranginq between 80 and 100 p.s.i.
impact blows in the range of 3120 blows per minute can be achieved with a force range of about 1,22~ ft/lbs.
Grooving of the surface may also be performed by judicial selection of the relative relatin of fore and aft hammers, and whether they are placed in activated or inactivated status. Referring to figure 13, grooves into the surfaces may be cut having different crossectional profiles than that shown in figure 10.
.
MOBILE APPARATUS FOR REVERBERATI~G
SURFACE S
INVENTOR
Ronald A . W . CLARKE
ABSTRA(::T OF THE DISCLOSURE
. . . _ A mobile impacting device which is self propelled at controlled speeds has a plurality of independently con-trollable hammers which drive percussion tools into impacting blows with the surface to thereby erode the surface and or cut grooves and or cut holes. By the relative control of the speed of travel of the device the number of hammers actually impacting ~he surface and the position of the hammers erroding the surface, cutting grooves into the surface, or hole cutting can be achieved.
By the particular cantilever coniguration of the hammers relative to ~he contact running wheels of a mobile device, the device can accom~odate erosion groove cutting pr hole cu*ting in confined areas. In fact it also has the advantage in bump cutting, that is the elimination of surface disconti-uity.
.
., This invention relates to a mobile apparatus for reverberating surfaces.
More recently, it has become known that if a rigid surface is struck rapidly with a series of impact blows, the surface impacted and its substrate, are stressed, during impact into compression and during thè interval between stikes (impacts) the substrate and surface reElex into tension. Some materials for example concrete or rock reflex better under compression than tension; thus the series of impact blows to the concrete surface will erode the surface away but will not injure ~he substrate. The absence of damage to the underlying structure and substrate, is due to the fact that when each impact tool strikes the surfa~e, it causes the material within its area to deflect, thereby creating a momentary and localized compression of the material. The compressive strain of the material is mainly elastic and therefore almost immediately given up in generating a rebound in the material thereby causing the material to pass through its relaxed state into one of tension nearIy equal to the initial compression. As the material is much weaker in tension than compression, it is unable to a~hieve the level of tensile strain corresponding to the previous compressive strain. The material consequently fractures, the elastic energy being given up as kinetic energy and fragments thrown out of the s~rface o~
the material. This percussive action takes place with great rapidity. This allows for the treatment of concrete surfaces for removal of surface laitances or imbedded contaminants such as rubber which if severe enough will render the surface slick reducing the inherently acceptable level of the static coefficient of friction for the surface. This is undesirable when the surface is a heavily travelled one such as an airport runway or motorways (highways) since the reduction in the coefficient of friction for the surface reduces traction of tires and hence safety tolerances.
It is also known that certain concrete motorways or runways and in particular bridge deckings, such as those carrying motorway surfaces tend to disintegrate most notably as a result of the combiried influences oE freezing and thawing cycles, moisture and salt. These conditions are typically encountered in the temperate regions of the globe and are notable in environments similar to Ontario, ~anada where the yearly freezing and thawing cycles extend over many months commencing in mid October and extending through the winter into early or mid April and sometimes ZO even May. W~th moisture converting to ice, and binding itself to the insites of the concrete surface, concrete surface breakdown is inevitable. This ~reakdown is even encouraged when calcium chloride is used, by road crews, to melt the ice so that the road surface~ will turn into a wet but not an icy state, a more desirable condition for travelling of vehichles.
Thus, regions in such surface which have disintegrated must be removed prior to restoration.
Typically this has been done by jack hammers~
When in England, I developed a stationery device which provides a rack with reciprocating hammers/ and percussion tools, which impact the surface over a sufficient elapsed time to cut holes of controlled shape and depth into concrete. 'm e percussion tools are travelled in relative orthoginal direction in a frame of the stationery device in order to impact over a control region. It was ~hen an easy matter to remove the debris (detritus) from the hole, coat the hole with a bonding agent, and insert a preformed or precast slab into the hole - the repairs were performed in unprecidented time.
~ owever, on reflection, this technique is inadequate, not because controlled impacting does not per~orm controlled cutting well, but rather on the contrary~
Controlled cutting is performed so well as to shape of aperture and its depth, that my earlier stationery device performed the cutting task archaically and wholly inadequately because it had to be manhandled from operational site to operational site, when site changes where desired; further in operation the de~ice had to be mounted or~affixed to the road surface prior to use.
I then conceived of a mobile device with impacting hammers mounted between fore steerable wheels and rear driver wheels.
I have now conceived of a device which is self-propelled at controlled speed and has a plurality of independently controllable hammers which drive percussion tools into impacting blows with the surface; that is into the surface subadjacent to each tool. By relative ~ontrol of both speed of travel of the device, zero to a maximum, and the number of hammers impacting the surface, on the one hand~ larger surface areas may be stripped of surface laitances; or, on the other hand, controlled shapes of apertures and of depths may be cut into the surface or substrate as desiredO By cantilever configuration of the hammers, relative to the surface contact running wheels of the devlce, the device travels the percussion tools over the surface to be treated in advance of the contact runnin~
wheels. Further benefits are thus achieved. Firstlyl the a~ility to impact the surface in confined reyions as commonly found at corners of a surface which mate to adjoining uprising walls and secondly the ability to smooth out surface discontinuities ("bump cuttingl') as is commonly found between sheets of adjoinin~ surfaces which have experienced localized settling or heaving.
The invention also achieves a device which may cut holes into the surface of predetermined shape, size and depth.
Further-the invention achieves means for erroding surfaces by an essentially "dry process" and for facilitating the collection of detritus and thus eliminates any ~lurry that would otherwise be caused by the use of large amounts of waters necessary to flush away the detrikus. Wetting the impact surface is thus avQided as a wet state surfa~e causes slower cutting and erroding than on a dry surface. Thus the region above the surface of impact is to be treated with a vapour mi5t and preferably a sweeper sweeps the treated area thereafter.
Further collection of detritus is enhanced with a sweeper and a vacuum collection device which are integral to the device (vacuum eleaner).
The invention therefore contemplates a mobile apparatus for imparting percusive blows to an underyling surface over whieh the apparatus may travel comprising:
(a) carriage means having axles with running wheels engaging the surface by which the carriage may be travelled thereon;
(b) a plurality of adjacently disposed hammers mounted in a bank with percussive tools, depending from the hammers, located intermediate the bank and the underlying surface, the hammers responsive to a flow of eurrent through the hammer by which the hammer is activated to reciprocate the percussive tool into periodie contact with the surfaee~ and, (c) means for mounting said bank along one peripheral edge of the carriage means.
The invention will now be clescribed by way of example and reference to the accompanying drawings in whieh:
Figure 1 is a side elevation of an embodiment.
Figure 2 is a side eleYation of an alternative embodiment employing a rotary sweeper for removing debris.
~igure 3 is a seetion along III-III of figure 2.
Figurè 4 is a perspective of fore and aft hammer raeks and the means by whieh each of the hammers is relatively positioned.
Figure 5 i.s a perspeetive of the control means by whieh each of the hammers of figure 4 may be positioned.
Figure 6 is a circuit diagram of the eontrol circuit (for a single ore and aft hammer) by which they are aetivated into operational status for reciprocation.
Y~
Figure 7 is a plan view of an embodiment of a hammer rack allowing relative positioning of fore and aft racks~
Figure 8 is a perspective partially in section of the racks adiustment means of figure 7.
Figure 9 is an elevation, partially in section, of the for laterally tracking means of figure 7.
Figure 10 is a representive profile section of a surface grooved by the hammers of figure 7 through 9 when positions Dl and D2 are coincident.
Figure 11 is a plan view of an alternative means for laterally tracking both banks of hammers relative to the frame using pneumatics or hydraulics.
Figure 12 is a partial view in elevation of the racks of figure 11 indicating the full "offset" position when the percussive tools of one bank overlap in part those of the other bank.
Figure 13 is an elevation o~ a segment of the racks oE
figures 11 and 12 showing alternative means by which grooving of the surface may be obtained ~via independent vertical control~, and the grooved section cut into the surface and substrate.
Figure 14 is a side view in elevation of th-e embodiment of figure 2`illustrating the hydraulic circuit for misting.
Refering to figure 1 a mobile impacting vehicle 10 comprises a frame 11 attached to the front and in cantilever relationship to.a following carriage 12, which carries an axle with a pair of fore running wheels 14 and a second axle carrying a single aft running and steera~le wheel 15, which acts as a turnin~ wheel for the vehicle since it is connected by appropriate linkages 15a to a sterring wheel 18 ~L~3~
for driver control. The actual vertical members to which the frame 11 is attached are shown as members 12' and are integral with the carriage 12. A seat 19 is placed on the top of the carriage 12 for the cornfort of the driver and a plurality of controls 20 which operate the two rows of impacting hammers 30 and 31 located in the lower regions of the frame 11 in a manner which will shortly be described;
control 21 governs the forward or rearward direction of drive. The carriage is driven into travel by an airmotor 23 which transmits motion via pulley 22 and drive belt 24 to a pulley, 14a, on one or both of the fore wheels 14.
Control lever 21, by means not clearly shown in the figures, controls the flow of air into the air motor 23 so that the vehicle 10 may move in a forward or rearward direction under variable and controlled speed.
In the embodiment of figure 1, frame 11 carries two banks of hammers 30 and 31 a single rack 32, so that the hammers are positioned along or across the front pheriphial edge of the vehicle. Each hammer 30, 31 is suspended from the rack 32 to depend downward and expose its hammer shaft 36 on which is carried an cylindrical impacting or compression tool 34 at the end thereof. The tool has a diameter of about 5-6.5 cm. Each hammer 30 or 31 communicates by its own pneumatic conduit 38 to either fore or aft manifolds 39. Each manifold communicates through an interconnecting~manifold conduit 42, to a feed pipe 44, which is connected to an outboard source of pneumatic pressure such as that commonly available from a portable air compressor (now shown). The air compressor (not shown) may be conveniently pulled from a hitch 50 affixed to the rear 3~
of the vehicle lO. In the embodiment of figure l the rack 11 is integral the frame ll which is bolted onto the front pheriphial edge of the carriage 12 as shown. Thus, it is fixedly positioned outboard and in advance of the running wheels 14, hence, in cantilever fashion. The ~hammer) rack 32, on the other hand, may be fixed relative the frame ll but is preferred to be ree to travel ~p and down opposing internal margins of the vertical end members 13 from which the frame is fabricated. This allows the rack 32 and the hammers to be positioned when in operational use into that position shown in figure l; when not in operational use into that position shown partially in phantom. Guide wheels 17 are provided at the upper margins of the rack 32 to guide the rack up and down the opposite facing vertical members 13. The rack 32 is moved up and down under pneumatic and/or hydraulic control by means of a piston cylinder 37 and its moveable piston rod 39; the rod 39 connectin~ to the upper face of the rack 32 through a pivot connection and the cylinder 37 attached to an upper cross member 16 of the frame ll. ~or stability during operation the rack rests on fore and aft lower horizontal end members 29.
Typically, in operation, compressed air is provided to the feed pipe 44 and distributed by the manifold conduit 42 into the fore and aft manifolds 39; thence, into the individual pneumatic conduits 38 to each individual fore hammer 30 and each individual aft hammer 31. The means by which the pneumatic hammers are activated thereby may be conventional; or, as disclosed in my co-pending Canadian Patent ~pplication, Serial No. 273,457, filed ~ March, 1977, g _ 7~
entitled 'Method and Apparatus for Removal of Contaminenets from Surfaces of Materials'. In general, any other means for driving the impactiny tools into reciprocation may be used~ for example electric current operating reciprocating hammers or hydraulics.
I prefer that the mean distance PD between fore running wheels 14 and the region between fore and aEt hammers (mean impact region 53) to be as short as possible say about 7-12 inches (17cm - 30cm~. This will allow positioning of the impact region 53 into corners with ease with the only possible untreatable area being the region in advance of the impact region and behind the front vertical member 13.
In another embodiment, referring to figures 7 through 9, the rack 32 may be provided with a longitudinal slot 33 extending essentially the width of the rack 32 and with an overlaying movable hammer carrying plate 35. The aft hammers 31 then project through the slot 33 but are attached to the overlaying hammer carrying plate 35. To this plate 3~ is attached, at one end a threaded bearing 47~ Through the bearing 47 extends a threaded shaft 46 which also extends through an uprising threaded anchor plate 48 attachèd to the rack 320 The threaded shaft 46 terminates at a hand crank 49 located at its other end~ By rotating the hand crank 49 the relative position of the aft hammers 31 to the fore hammers 30 is changed. In this way the centers of the fore and aft hammers may be deviated under adjustment by the dimension indicated as D in figure 7; that is, from position D~ to Dl. When the aft hammers 31 are located with centers at D2 as shown there is a relative overlap (OL) of each percussive tool 34 depending from the aft bank of hammers 31 relative those of the fore bank 30~
The overlap can be controlled or eliminated by turning the crank whereupon the centers of the aft bank oE hammers 31 are moved from D2 (the overlap position of the percussive tools) into position Dl (the registry position of fore and aft hammers). In the former position D2 the fore and aft running wheels 14 and the region between fore and aft hammers 30, 31 are not irl registry; they impact different underlying surface regions during surface transverse of the underlying surface~ Thus there is i~pact to the total underlying surface.
By altering the relative position of the aft hammers relative the fore hammers, the centers of the fore and aft hammers may be placed in registry~ eg. along line Dl, In ~his way the centers of the fore and aft hammers will be in registry and when the vehicle 10 moves forward the tools 34 of each bank will impact the same surface; gouging and grooving of the surface will result as per figure 10. The ~0 depth of each groove will depend on the speed of traYel and the number of blows impacted to the surface. The grooYe width is ~20L whilè the step is ~-20L where ~ ~s the diameter of the tool 34. Needless to say, with different relative positions of ~he centers of fore and aft hammers the profile of the grooves may be altered.
Referring,now to yet a further embodiment and to figure 2, the mobile vehicle 10 is almost identical to that of figure 1 save in the following respects. Note between the fore wheels 14 and rear wheel 15 is a rotary broom 52 driven by belt 53 via the same pulley 22 from the airmotor 23. It could as conveniently be driven by an inde~endent power source ~not shown~. Further a vacuum cleaner 55 is mounted on top of a water tank 60~ The vacuum cleaner 55 communicates to a collection shute 54 mounted aft of the rotary broom 52~ Driven by conventional means ~not shown) the vacuum cleaner 55 removes via the shute 54 detritus dislodged from the surface as a result of the percussive tool action and the rotary sweeper.
Alternatively, while not confined to the embodiments disclosed in Figures 2 and 3, the frame 11 and its racks of hammers may be fabricated with still additional featuresO
The frame 11 may be adapted for vertical movement relative to the carriage 12. As such, each rear vertical member 13 extends, as shown in s~ction in figure 3, into a I ~male grooved track 113, while the front vertical carriage arm 12 extends into a complimentary mating male runner 112.
As such, the Erame 11 may be movled into its operational position as shown in Fig. 2 or into its rest po ition for travel, as shown in the phantom position 96, for travelling between operational sites. The hammers 30 and 31, en mass are thus lifted ~rom operational to non-operational status.
The means o~ lifting may be accomplished by convenien$ mean~
for example a lift mechanism 95 includes a cylinder 90 whose bottom is affixed to a horizontal cross member 12N
interconnecting the lower termini of the verticàl uprising members 12'. The cylinder 90 has a pusher rod 91, the free end of which carries a parallel gear train 92. Two chains 93 are each attached, at cne end, onto the carriage 12, and threaded over the parallel gear train 92 and terminate at dead soldiers 94 intergal with the vertical members 13. As the cylinder extends the piston 91, the gear train 92 moves upward, and the whole frame 11 is moved to its upper most position 96 shown in phantom.
In yet an alternative embodiment, the hammers and racks may be of different configuration.
Firstly, the single rack 30 can ~e eliminated in favour of a dual rack cage, a fore rack cage 130 and an aft rack cage 231. Each cage has its own rack floor, respectively 13Z and 232; front and rear walls, 133, 133'; 233, 233~; and upper covers 134, 234 which terminate at bushings. These bushings are respectively carried by fore and aft cage support bars 135 and 235 carried by ~not accurately shown~
an upper transverse member T. Tbis completes cage suspension within the frame 11.
Each fore hammer 30 is operationally positioned into the rack plate 132 by its o~n positioning device; namely a pneumatically positioning cylinder and piston assembly 60;
similarly aft hammers 31 into the aft rack plate 232 by penumatic assemblies 61.
2n Referring now to figures 2, 4, 5 and 6, the position o~
each hammer, fore and ~ft, in their respective racks, i5 controlled by a control bar CB, which extends across the lower front face of the frame 11. A plurality of levers 1, or 0 indicating fore or aft racks, and (a through k indicating linear position along each rack) independently actuate each c~inder 60 or 61 into rest or operational status for the respective hammer. Thus, referring to figure 4, hammers 30e through 30k and 31d through 31k are shown at rest while 30a through 30d and 31a throuyh 31c in operational status.
The circuit diagram of figure 6 is representative of the communication by which the hammer is positionally located at rest or in operational status. Namely, from the manifolds 39 a direct feed ta each hammer 30 or 31 is achieved by its own pneumatic conduit 38 as earlier disclosed. The feed' may be add'itionally turned on by an appropriate stop cock or the like ST located in the line~
An auxiallary feed AF communicates with the fore manifold 39 and is the central feed to the control box CB.
Each piston 60 has its own activating conduit fi4 and inactivating conduit 66 which is connected to its own pneumatic switch lever 1 wbich has a common communication~
now shown, via the control Box CE~ to the auxiallary feed A~. The actual lever 1 will be one of la through lk depending upon the positional location of the hammer in the rack~ The activated or non-activated status of each hammer is thus governed by the upward or downward postion of the lever 1. Similarily, for the rear hammers 31 and their assemblies 61 the same are controlled via the conduits 65 and 67 and the appropriate position of levers 0 for each positional location a through k, ~ urther each of the fore and aft cages may be oscillated relative to each other and to the frame 11. Thus each cage has its own oscillitory means; namely, a cylinder 70 with moveable rod 71, the free end of which ~72~ connects to a thrust pl~te extension 73 integrally attached to the cage. The cage itself slides, in response to actuation of the rod, along its own support bar 135 or 235 as the case might be, with the aid of the cage bushings. The cylinder and rod of course may be pneumatic, hydraulic or otherwise.
These embodiments are ideally suited for erroding the total surface area underneath the main frame or alternatively cutting holes or grooves~
In order to facilitate cleaning oE the treated area, by the vertical 10 and referring to figure 2, the vehicle 10 is fitted with a rotary broom 52 of conventional style mounted between the front and rear wheels 14 and 15. The rotary broom is activated of course by its own pulley 53 communicating as well to the air motor 23 and its drive pulley 22. The debris which the broom sweeps up off the treated surface is collected by shute 54 connected to a vacuum device 55 of conventional style, Thus the detritus is accumulated in the vacuum cleaner box 55. In order to reduce the amount of free flying dust and detritus imparted into the atmosphere with each stroke of the impact tool 34, and referring to figures 2 and 14, there is a hydraulic misting circuit comprising a transverse bar 65 mounted between fore and aft hammers with a plurality of spacily disposed misting nozels 67 depending therefrom. The transverse bar 65 communicates by conduit, shown, to a tank reservoir 60 holding water. Air from the manifold 35 is injected into the water reservoir 60 and thereby causes it to be pressurized thereby conveying the water out of the misting nosels 67 to create a mist M in that region and in the space just above the strike region 53. The mist captivates free-dust and flying detritus resulting in a cleaner operation while at the same time leaving the strike surface (hammer lane) dry.
When tool surface area under the frame 11 (hammer lane) is to be treated, fore and aft hammers are positioned in ~ 15 offset as shown in figure 12, so that the peripheral edge of the tandum hammers overlap the adjacent hammer of the other rack or cage. The perferred overlap, OL, is about 2mm when the tool head diameter is about 5 - 6.5 cm.
When the holes are to be cut, for example H of figure 4, this may be achieved as follows. ~ammers 30a through 30d r and at hammers 31a through 31c are placed in the activated status. The hole as shown will be cut. This requires that both fore and aft racks 32 and 232 must be oscillated relative the rame ~if both racks are to be used as shown). The oscillation of the racks to registers and unregisters the centers of each of the fore and aft cut-ting hammers. Expressing this another way, it is necessary to reduce the dimension D as seen in figure 7, from 0 to its maximum displacement and back again. (The manual operation of this facility, as earlier described in reference to the embodiment of figures 7, 8 and 9 is cumbersome)~ Hence, I
prefer referring to the embodiments of figure ll, to oscillate both racks. There the aft hammers 30 are driven to and fro as are the fore hammers under the control of their own reciprocating cylinders 70, and rods 71 which connected to their thrust plate extensions 73 integrally attached to either the fore cage 130 or rea~ cage. In this manner the cages are driven, relative to the frame back and forth as generally indicated by the arrows in figure 4.
The shape of the hole H is cut as shown; the depth of the hole is governed by the duration of and extend of the impact blows.
A slower but acceptable method of cutting a hole H
3~ would be to deactivate all fore hammers 30 and to have but a single reciprocating cylinder 70, rod 71, rod head 72, connecting to a single thrust plate extension 73 integrally attached to the single cage eg. cage 231. The fore cage 130 would be fixed and not capable of oscillation. The f~re hammers would be placed into the inactive position~
The rear hammers 31 a, b and c, would be activated and the rear rack oscillated, while the truck lQ removed firstly forward and then rearward so as to cut the hole to its.
desired length; the depth of the hole of course would be controlled by the number of passes forward and backward of the hammers and of course the rapidity of the strike and the strength strike impact blow. Typically with air pressures on the pneumatic hammers ranginq between 80 and 100 p.s.i.
impact blows in the range of 3120 blows per minute can be achieved with a force range of about 1,22~ ft/lbs.
Grooving of the surface may also be performed by judicial selection of the relative relatin of fore and aft hammers, and whether they are placed in activated or inactivated status. Referring to figure 13, grooves into the surfaces may be cut having different crossectional profiles than that shown in figure 10.
Claims (15)
1. A mobile apparatus for imparting repetitive percusive blows to an underlying surface over which the apparatus may travel comprising:
(a) carriage means carrying at least three running wheels arrange into fore and aft wheels that engage the underlying surface over which the carriage may travel thereon; and, (b) a plurality of adjacently disposed hammers arranged into at least two relatively parallely positioned banks, the hammers carried by the carriage in advance of the fore wheel and mounted with some of said hammers carrying percusive tools depending from the hammers, the hammers responsive to a flow of current through the hammer that activates the tool to reciprocate the tool into periodic violent percusive contact with the surface; the hammers are positioned in each rack so that the special distance between adjacent edges of tools in one rack is less than the diameter of each such tool.
(c) means for injecting water vapour into that space intermediate the bank and the surface;
(d) means for positioning each hammer, relative to the surface, from an operative position at a lower elevation to an inoperative psotion at a higher elevation;
(e) sweeping means mounted between the said axles and carried by said carriage means said sweeping engaging said surface and for sweeping the same after impact by said hammers.
(a) carriage means carrying at least three running wheels arrange into fore and aft wheels that engage the underlying surface over which the carriage may travel thereon; and, (b) a plurality of adjacently disposed hammers arranged into at least two relatively parallely positioned banks, the hammers carried by the carriage in advance of the fore wheel and mounted with some of said hammers carrying percusive tools depending from the hammers, the hammers responsive to a flow of current through the hammer that activates the tool to reciprocate the tool into periodic violent percusive contact with the surface; the hammers are positioned in each rack so that the special distance between adjacent edges of tools in one rack is less than the diameter of each such tool.
(c) means for injecting water vapour into that space intermediate the bank and the surface;
(d) means for positioning each hammer, relative to the surface, from an operative position at a lower elevation to an inoperative psotion at a higher elevation;
(e) sweeping means mounted between the said axles and carried by said carriage means said sweeping engaging said surface and for sweeping the same after impact by said hammers.
2. An apparatus as claimed in claim 1 wherein the current is a flow of fluid.
3. An apparatus as claimed in claim 1 wherein the current is a flow of gas.
4. An apparatus as claimed in claim 1 wherein the current is a flow of compressed air.
5. An apparatus as claimed in claim 1 including means for moving one blank relative to the other.
6. An apparatus as claimed in claim 1 with means for relatively positioning the bank of hammers at a predetermined distance from the surface.
7. An apparatus as claimed in claim 1, 2 or 5 including a frame attached to a peripheral margin of the carriage means, a moveable rack which carries the bank of hammers, mounted to travel in the vertical in said frame and means for moving said rack in said frame.
8. An apparatus as claimed in claim 1, 2 or 5 including a frame attached to the peripheral margin, the frame including uprising front and rear lateral members, a moveable rack, carring the bank of hammers, mounted to travel in the vertical up and down the frame, via rollers adapted to run up and down the lateral uprising members, a cylinder with piston rod assembly one end of which is attached to the rack, the other to the frame, and means for driving a fluid into the cylinder whereby the special distance between the ends of the assembly is changed and hence the positional location of the rack within the frame is altered vis-a-vis the surface.
9. An apparatus as claimed in claim 2 or 3 including means for injecting water vapour into that spac e intermediate the bank and the surface.
10. An apparatus as claimed in claim 5 including a rack moving assembly including a cylinder, and moveable rod with free end, the free end of the rod and the opposite end of the cylinder respectively attached between frame and and one of said racks and means for activating the cylinder thus moving the rod in the cylinder whereby the relative position between the ends is changed and hence the relative positions of the rack and the hammers thereof vis-a-vis the frame.
11. The apparatus as claimed in claim 10 wherein there are a pair of rack moveable assemblies, each respectively attached between the frame and its own rack, whereby the racks may be oscillated independently of each other.
12. An apparatus as claimed in claim 6 or 10 wherein the hammers are positioned in each rack so that the special distance between adjacent edges of tools in one rack is less than the diameter of each such tool and means for positioning each bank of hammers in offset whereby the surface region struck by hammers of one bank and adjacent hammers of the other bank in part overlap.
13. An apparatus as claimed in claim 1 or 5 including a plurality of hammer positioning assemblies including a cylinder and a moveable assembly having one end carried by the frame, the other end attached to its own hammer and means for independently activating each of such assemblies to independently locate said hammer into an operational position at a lower elevation or an inoperative position at a higher elevation.
14. The apparatus as claimed in claim 1, 2 or 5 including sweeping means mounted between said axles and carried by said carriage, said sweeping means engaging said surface and for sweeping the same and vacuum means for removing detritus swept by said sweeping.
15. The apparatus as claimed in claim 1, 2 or 5 including a rotary broom mounted between said axles and carried by said carriage, means for rotating said broom whereby said rotary broom engages said surface and vacuum means for removing detritus swept by said sweeping.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000297367A CA1139975A (en) | 1978-02-21 | 1978-02-21 | Mobile apparatus for reverberating surfaces |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA000297367A CA1139975A (en) | 1978-02-21 | 1978-02-21 | Mobile apparatus for reverberating surfaces |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1139975A true CA1139975A (en) | 1983-01-25 |
Family
ID=4110826
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000297367A Expired CA1139975A (en) | 1978-02-21 | 1978-02-21 | Mobile apparatus for reverberating surfaces |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA1139975A (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0566752A1 (en) * | 1992-03-26 | 1993-10-27 | Joseph Vögele AG | Extendable roughening screed |
| CN105544499A (en) * | 2015-12-29 | 2016-05-04 | 河南四海建材设备有限公司 | Small tamping machine |
-
1978
- 1978-02-21 CA CA000297367A patent/CA1139975A/en not_active Expired
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0566752A1 (en) * | 1992-03-26 | 1993-10-27 | Joseph Vögele AG | Extendable roughening screed |
| CN105544499A (en) * | 2015-12-29 | 2016-05-04 | 河南四海建材设备有限公司 | Small tamping machine |
| CN105544499B (en) * | 2015-12-29 | 2017-09-22 | 河南四海建材设备有限公司 | Small-sized ramming machine |
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