CN1195383A - Soil compactor with stabilising wheel system - Google Patents
Soil compactor with stabilising wheel system Download PDFInfo
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- CN1195383A CN1195383A CN96196790A CN96196790A CN1195383A CN 1195383 A CN1195383 A CN 1195383A CN 96196790 A CN96196790 A CN 96196790A CN 96196790 A CN96196790 A CN 96196790A CN 1195383 A CN1195383 A CN 1195383A
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- 239000002689 soil Substances 0.000 title abstract description 6
- 230000003019 stabilising effect Effects 0.000 title description 2
- 238000005056 compaction Methods 0.000 claims abstract description 41
- 230000033001 locomotion Effects 0.000 claims description 63
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Classifications
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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
- E02D3/026—Improving by compacting by rolling with rollers usable only for or specially adapted for soil compaction, e.g. sheepsfoot rollers
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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
- E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
- E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
- E01C19/23—Rollers therefor; Such rollers usable also for compacting soil
- E01C19/26—Rollers therefor; Such rollers usable also for compacting soil self-propelled or fitted to road vehicles
- E01C19/266—Rollers therefor; Such rollers usable also for compacting soil self-propelled or fitted to road vehicles fitted to vehicles, road-construction or earth-moving machinery, e.g. auxiliary roll readily movable to operative position ; provided with means for facilitating transport; Means for transporting rollers; Arrangements or attachments for converting vehicles into rollers, e.g. rolling sleeves for wheels
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- Engineering & Computer Science (AREA)
- Structural Engineering (AREA)
- Life Sciences & Earth Sciences (AREA)
- Civil Engineering (AREA)
- Environmental & Geological Engineering (AREA)
- Agronomy & Crop Science (AREA)
- Architecture (AREA)
- Soil Sciences (AREA)
- General Life Sciences & Earth Sciences (AREA)
- Mining & Mineral Resources (AREA)
- Paleontology (AREA)
- General Engineering & Computer Science (AREA)
- Road Paving Machines (AREA)
- Investigation Of Foundation Soil And Reinforcement Of Foundation Soil By Compacting Or Drainage (AREA)
Abstract
The invention concerns a self-propelled impact compaction machine that includes a chassis (20) with a prime mover thereon. The chassis (20) carries ground engaging wheels (21) at least some of which are driven by the prime mover. Compaction of soil is achieved by one or more impact compactor masses (24) which have out-of-round shapes so as to apply periodic impact blows to the soil surface when rolled over that surface. The mass or masses (24) are connected resiliently to the chassis (20) and define a compaction track width measured from one lateral extremity of the mass or masses (24) to the opposite lateral extremity of the mass or masses. The ground engaging (21) wheels of the chassis define a maximum wheel track width which is not substantially different in magnitude to the compaction track width, with the desirable result that the chassis (20) enjoys substantial roll axis stability.
Description
The present invention relates to adopt be disclosed in US2 first the soil compression of the compactor of the cardinal principle type in 909,106.
" tamping roller " that be used for above-mentioned United States Patent (USP) first is meant a kind of compactor that adopts non-circular compacts, when drawing its walking on the ground, can produce series of periodic on the ground and ram.A series of separated salient points are arranged in the outside of ramming the roll-in entity.There is a recessed portion each salient point back at described external surface, and in each recessed portion back a compaction plane is arranged.For example, be pulled in when walking on the ground by tractor when ramming roller, it is in each salient point place lifting, and in its landing downwards forward during by salient point, the result is produced ground by compaction plane and once rams.
The effect of compacts is to accumulate potential energy during in the lifting of each salient point place at this compacts, and disengages this energy to ram form when this compacts falls and rams ground by compaction plane.In essence, being connected between tractor and the compacts is flexible, so as compacts can take place during by each salient point necessary forward with downward landing campaign.
Already commercially produce out the roller of ramming that has adopted single compacts, and successfully be applied to civilian mechanical industry.Singly ram body with what be disclosed in that compound in the European patent 0017511 ram that roller replaced the above-mentioned type.
Figure 1 illustrates three binarys and ram the lateral view of roller and tractor thereof, wherein, removed one of them and rammed body to show the element between two compacts.Fig. 2 rams the rear elevation of body for this, and Fig. 3 is its plan view.
In Fig. 1,2 and 3, vehicle frame 1 is connected by common axis assembly 3 between two compacts between two compacts 2.Shaft assembly 3 is made up of an outer tubular axle and an interior torsion bar (not shown), keeps the synchronous rotation of compacts by it.Interior torsion bar is an elastic component, so that limited amount reversing only arranged between compacts.
Changeing assembly 3 is to be connected with vehicle frame 1 by the connected system that roll extrusion is handled.This connected system comprises a draw bar 4 that is fixed on an end of axle 3, and is connected in rotationally on the lower link 5, rotates so that pitch axis only can take place.
The lower end of lower link is connected on the vehicle frame 1, rotates so that pitch axis only takes place, and its upper end is connected with a draw-gear 6, and the effect of this draw-gear is traction and damping.On vehicle frame, be equipped with two pairs and drive carrying-off wheel 7.Hydraulic lift(ing) cylinder 8 running between vehicle frame 1 and axle 3 is so that lift from ground with compacts when roller is rammed in transportation.
Vehicle frame is connected on the tractor 10 by a joint coupling 9, and making tractor and ram can be around all three axle relative motion between the roller.Therefore, connector 9 can make to be rammed roller and does rolling, break away and elevating movement, wherein " rolling " be meant the rotation of impact roll around the forward and backward direction of motion.
The roller of ramming by the tractor traction shown in Fig. 1,2 and 3 is commonly used at present.Compacts can have three, four or five shapes usually, and weight is the 3-10 ton usually.
Referring to Fig. 4, the size of R and r is respectively 1100mm and 900mm usually.Represent with M.g.h that at the potential energy that accumulate because of the compacts lifting at the salient point place wherein (unit: rice), M is the quality of representing with Kg to h=R-r.Therefore, (10, compacts 000Kg), the energy that is used at every turn ramming are 10000 * (1100-900) * 9.81=19,600J, or 19.6KJ for 10 tons of counterweights.
For the roll squeezer of ramming of (being 19.6KJ) of the above-mentioned type, the width of compacts shown in Figure 3 is generally 1m, and the spacing between compacts also is 1m, and therefore, the overall width of this machine is 3m.Tractor 10 can be heavy 8 tons.Find in practice, must make the compacts spacing be equal to or less than the width of each compacts, so that when carrying out roll-in for the second time, can cover the left gap of roll-in for the first time with a compacts.Therefore, the width of each compacts also limits the gap between compacts, and this requirement is restricted to a little wheelspan with width 12 (Fig. 2 and 3).
Given above-mentioned sized data is to want the design main points of holding capacity and stress intensity in order to establish ramming roller when work machine element.
When roller work was rammed in discussion, it was favourable that the above two types mode of operation of described machine is taken into account.At first be " delivery " pattern, wherein, compacts is lifted from ground under the effect of lift cylinder 8 (Fig. 1), so that can drive or transport and ram roller under situation about the ground generation not being rammed.The quality of compacts is by 7 carryings of the running wheel among Fig. 1 under this pattern.Secondly be " compacting " pattern, wherein, oil cylinder 8 retractions, compacts is placed on the ground, and like this, when the traction vehicle frame, compacts rotates and the ground generation is rammed.
Illustrate that at first general type rams the delivery pattern problem of roller.Again referring to Fig. 1,2 and 3, overcome the stability of crossing the component of rotation around roll shaft and depend on wheel fully.Be appreciated that as indicated abovely, vehicle frame is connected with draw bar 4 with lower link 5 by pivot, and draw bar is connected on the shaft assembly 3 at last, does not allow relative roll shaft motion between vehicle frame and axle.In Fig. 7, the power of compacts center of gravity is passed through in line of vector 16 expressions, in conventional machine, and the alternate 2m of two compacts.Line of vector 17 expression is from the reaction force of tire, the two tires 0.5m of being separated by usually.Owing to have to wheel is placed on the inverse proportion that restriction in the design between the paired compacts has caused 2.0m and 0.5m.Fig. 7 represents the compacts that run into and the inversely proportional influence of ground-engaging wheel width when ramming roller by common uneven ground condition.When wheel 7 enters little ground pit, can cause the undue roll shaft motion of the compacts that has amplified.The result makes a compacts ram ground at point 19 places.This least wishes to occur, because this can cause damage to the surface of moulding or part moulding or to machine itself.Find in the practice that the elasticity that is used for the rubber tyre on the wheel 7 can increase the weight of above-mentioned undesirable roll shaft motion, and the vibration that causes compacts to be tossed about around roll shaft usually.Joint coupling shown in Figure 19 between vehicle frame and tractor can not produce resistance to the roll shaft motion of connected compacts.
But, the practical operation when roller is rammed in use requires that to be machine will adopt the delivery pattern to transport with appropriate speed (being preferably greater than 20km/h) from a workplace to usually at a distance of several kms another workplace far away the time.But, for existing binary machinery, the speed that reality is delivered pattern because above-mentioned undesirable roll shaft moves is limited in less than 5km/h.
Owing to another kind of reason also needs to be implemented in roll shaft stability under the delivery pattern.Imagine a machine and under the compacting pattern, work,, be generally 20 times to realize repeatedly compacting process.Ramming roller for one therefore only can, when each compacting process finishes, must make machine turn to, so that carry out the compacting process of backhaul along a direction compacting.The required space of divertical motion is generally 3 or 4 times of machine overall width, does not have so big space usually.In addition, it is uneven that the ground of steering position can be interfered and become, and makes to ram the roller deceleration and the driver is not felt well, and increases the weight of wearing and tearing and reduction productivity ratio to machine.Owing to the inhomogeneities that rolls makes that ramming the roller steering position can not be densified to usually and meet technical requirements.If when no longer each compacting process finishes machine is turned to, can be with compacts jack-up, make it be in the delivery pattern, and the fast return starting point makes compacting process next time, therefore, can improve the operating efficiency of machine greatly, in some narrow subgrade construction such as railway bed and check dam, work is normally carried out on the height of projecting environment, and therefore, the compacting machine that use need turn to for the space of several times of himself width is unpractical.
Obviously, need make compacts under the delivery pattern, have suitable stability, and accurately control carriage return speed.Ram in the roll structure at common binary, by as Fig. 1,2 will ram roller with the joint coupling 9 shown in 3 is connected with a four-wheeled tractor, and its reversing process is identical with the carriage return process of tractor: owing to worrying that jack-knifing and control inaccuracy slow down carriage return speed.
When working, found the defective of existing catamaran design with above-mentioned delivery pattern.One of purpose of the present invention is, supports compacts to being the delivery pattern in sufficiently stable mode, thus can be comparatively apace on unestablished road surface or the direction transportation forward or backward of flexible pavement upper edge, rare or do not have side-sway or damage the danger on ground.
Under the compacting pattern, the machinery shown in Fig. 1,2 and 3 also has following defective.In this structure, axle 3 interconnects with vehicle frame 1, does not have the degree of freedom around the relative motion of roll shaft each other, produces big stress because of shock loading on vehicle frame and connecting rod element.Make an explanation in conjunction with Fig. 5 and 6 pairs of this phenomenons.When machine works, compacts 2 rotates synchronously.If ground is smooth fully, compacts will be rammed ground simultaneously, and that connecting axle 3 will keep will be parallel to the ground, and along with continuing along with compacts raises of rolling.But, actually, ground is disorderly, and has the projection and the pit of random distribution.Fig. 5 represent a pair of nearside body by the projection shown in the gravel 13.Fig. 5 and 6 expressions, the center of impacting the compacts of gravel begins to raise, and axle 3 carries out roll shaft along arrow 15 directions thereupon and rotates.Example with rare impact gravel 13 in Fig. 5 and 6 is explained the roll shaft displacement.But, normally in service under the compacting pattern, the cave in displacement of the axis that can cause roller of the different soil from a side to opposite side has identical intensity of variation.The drop of 50mm is very commonly arranged between both sides, form circular roll shaft angular displacement, shown in the numbering among Fig. 6 15.One side can be approximately 30 milliseconds with respect to sink time interval of Any Digit (as 50mm) of opposite side.
Roll shaft angular displacement shown in the arrow among Fig. 6 15 relates to draw bar 4, decline bar 5 and vehicle frame 1 (referring to Fig. 1 and 3).Be appreciated that big roll shaft torsion and reconnect the stress that bar and frame elements produced and betide in the short time interval, be generally 30 millimeters because of this roll shaft displacement is transferred to.This of short duration roll shaft displacement (on the magnitude of 30ms) is called as " displacement of impact type roller ", and the stress that is produced thus is called as impact type roller stress.
The stress that is appreciated that the connected system of connecting axle 3 and vehicle frame 1 by above explanation increases with the vehicle frame quality.Therefore, vehicle frame is widened or any design of increasing the weight of on variation also all can relate to impact type roller stress problem.
The impact stress phenomenon needs to describe in conjunction with the work of ramming roller.Typical pentagon is rammed roller and is rammed ground about 2 times each second, and it produces 2 * 60 * 60 * 10=72000 time impact in the time of 10 hours when machine works.In 100 hours work of every monthly average, can produce 720,000 impacts.If each the impact all produces stress to machine part, 720000 secondary stress pulses will there be every month.The personnel that are engaged in Machine Design are clear, and the carrying out repeatedly of the stress of this magnitude can make hardware generation fatigue damage.The most important factor of permissible maximum stress number of repetition was the peak value of stress pulse before the decision hardware lost efficacy.Therefore, have acceptable application life (being generally several years), importantly be provided for reducing the device of peak stress in order to ensure machine.Serious stress peak value is to ram the roller displacement by what produce at the inertia of heavy frame elements, and is as indicated above.This just need be provided with a centerpivot on axle, allow the impact displacement of rotating the 2-4 degree in this way usually, and reaches heavy frame elements with the sufficiently long time interval, to alleviate other harmful stress.
The roll shaft displacement that compacts and vehicle frame make up relative tractor also can be owing to the distortion of ground side take place, but motion is quite slow, makes that the pivot 9 between the vehicle frame 1 and tractor 10 can bear among Fig. 1.This slower motion that does not relate to impact load is called as " roller displacement slowly ".
In above paragraph, set forth the problem harmful: at first to effective, the safe work of ramming roller of existing form, being the roll shaft instability problem under the delivery pattern, secondly is to ram the roller displacement problem under the compacting pattern, can produce serious stress thus.Therefore, the purpose of this invention is to provide and make impact type roll extrusion function to be suitable for construction machinery in the speed of the deployment in building site safety and be able to the accurately device of control ground operation in the forward and backward directions, for example described speed is about 20km/h, on it has the chassis of wheel paired compacts is housed.Simultaneously, the present invention also seeks to provide and alleviates when with the compacting mode operation because of ramming heavily stressed that the roll shaft displacement is produced.
According to the present invention, a kind of self-propelled impact compaction machine is provided, it comprises a chassis, a tractor that is contained on the chassis, be contained in the ground-engaging wheel on the chassis, drive by described tractor to the small part road wheel, and there is one or several impact compaction body to be connected with chassis elasticity, described one or several compacts forms a compacts track width, to its another side, and the ground-engaging wheel on chassis forms maximum wheel stitch width, the width and the no significant difference of this width and compacting track to this width from a side of described one or several compacts, therefore, the chassis has outstanding roll shaft stability.
Described machine preferably includes a pair of isolated compacts, and this compacts is bearing on the common axis that is connected with chassis elasticity, one or several is housed between the compacts on the chassis drives running gear.In this structure, the maximum wheel stitch width that is formed by the ground-engaging wheel on chassis preferably approximately equals or only is slightly smaller than the compacting track that the side direction outer rim by two compacts forms.The machine of this form of the present invention can also be included in the lifting gear of working between chassis and the compacts, is used for compacts is promoted to more than the ground, so that transport.
In a kind of form of the present invention, be preferably two compacts of the above-mentioned type, the chassis of machine is formed by single, whole, rigid structures.In this case, the driving of road wheel can provide the single driving shaft of power to realize by tractor.In this form of the present invention, the axle that supports one or several compacts preferably has a spot of degree of freedom of rotating relative to the chassis at least.Preferably provide buffer, to cushion the roll shaft motion on chassis relatively of described axle.
In the controllable form of another kind of the present invention, two compacts of same preferred the above-mentioned type, the chassis of machine has the front and rear that is hinged in vertical clinoid place together.Between dividing, described front and rear portions also preferably has a roll shaft pivot.Buffer preferably is set, so that its anterior roll shaft motion relatively at buffering rear portion, chassis in the predetermined slewing area of roll shaft at least.In this case, this machine can comprise a release mechanism, makes the rear portion surpass preestablished limit relative to anterior between moving period without rotating at the roll shaft between these two parts of buffering.
In each form of the present invention, the roll shaft buffer all can be regulated, to change the resistance to relative roll shaft motion.When carrying out transport model, the impact compaction body is raised built on stilts, and therefore, the possibility of toppling is bigger, and buffer is the resistance during usually greater than impact compaction body kiss the earth under work or compacting pattern to the resistance of roll shaft motion.In some occasion, buffer (being preferably hydraulic shock absorber) can manual adjustments, and in other occasion, the automaton of the control, braking or other system that depend on machine can be arranged.
In the type of attachment of this machine, the roll shaft pivot allows the front portion on the relative chassis, rear portion on chassis to do roller displacement slowly.In this occasion, this machine can also comprise auxiliary roll shaft pivot, and the motion of impact type roller has been considered in this design, and this auxiliary pivot is usually located at the connecting portion between described axle and elastic link, described elastic link connecting axle and chassis.In this occasion, pivot is also cushioned.In a kind of specific embodiments, provide pivot and buffering effect by the snubber of a kind of rubber or other elastomeric material.
Fig. 1-7 represents a kind of common binary tamping roller.In these figure:
Fig. 1 represents the conventional towed lateral view of ramming road roller, and a compacts is removed, to show the thin portion of vehicle frame and connected system;
The rear elevation of tamping roller in Fig. 2 presentation graphs 1;
The plan view of tamping roller in Fig. 3 presentation graphs 1;
Fig. 4 represents to measure the required parameter schematic diagram of drop of tamping roller;
Fig. 5 represents to ram the lateral view of a pair of compacts on surface, uneven building site;
Fig. 6 represents to ram the rear elevation of a pair of compacts on surface, uneven building site, and has indicated the angular acceleration direction of compacts and connecting axle assembly; With
Fig. 7 is illustrated in the distribution of weight schematic diagram by a pair of compacts under the delivery state of a pair of wheel supporting of being separated by not far; And the unstability when having shown on uneven ground operation.
Fig. 8-23 is only with the formal specification embodiment of the present invention of giving an example.Wherein:
Fig. 8 represents the T shape sole of tamping roller rigidity in accordance with the principles of the present invention, has the transmission control shaft;
Fig. 9 represents to have the floor map of the T shape sole of handling connected system;
Figure 10 represents the side elevation in partial section of tamping roller of the present invention, and a compacts is removed, to represent the detailed structure on work mechanism and chassis;
Figure 11 represents the plan view of machine among Figure 10, has omitted some details for simplicity's sake;
Figure 12 represents the rear elevation of machine among Figure 10, has omitted some details for simplicity's sake;
Figure 13 represents the broken section rear elevation of Figure 10 central roll axle pivot;
Figure 14 represents the sectional view of mechanism among Figure 13;
Figure 15 represents the lateral view of broken section of the tamping roller of another embodiment of the present invention;
Figure 16 represents the plan view of tamping roller among Figure 15;
Figure 17 represents the pivot of impact road roller shown in Figure 15 and 16 and the amplification view of clamp mechanism;
Figure 18 represents the fragmentary sectional elevation view of mechanism shown in Figure 17;
Figure 19 represents that draw bar and elasticity among Figure 15 ram roll shaft stress and weaken enlarged detailed with attitude reference device;
Figure 20 represents the end-view of mechanism shown in Figure 19;
Figure 21 represents the plan view of the central siphon among Figure 19, has indicated the location of flexible member;
Figure 22 represents the lateral view of another embodiment of the present invention; With
Figure 23 represents the detailed plan view of Figure 22 maincenter axis mechanism.
At first referring to Fig. 8 and 9, it has shown potential principle of the present invention.These there is shown in plan view is the sole 20 of the tamping roller of T shape.Steerable wheel 21 be installed under the lateral part 20A that is positioned at sole the axle 22 on.Axle 22 can be driven by a suitable motor and the transfer device that is positioned on the 20A of lateral part, and the seat and the control device that use for operating personnel also can be set thereon.In addition, sole can also be connected with tractor elasticity.
Another is taken turns 23 and is installed in the end of T shape sole web 20B with form free to rotate.This chassis frame plate is between compacts 24.Should be pointed out that the compacts close proximity, this is narrow permission of sole web 20B.Compacts interconnects, so that roughly synchronously rotated by a common axis 25.Can be at sole and other Connection Element (not shown) between the compacts with above the described common connector of 1-3 is identical in conjunction with the accompanying drawings.
In other embodiments of the present invention, singlely take turns 21 and 23 and can be replaced by the wheels on the relevant position.
Fig. 9 represents a kind of improved sole, and wherein, the lateral part 20A of sole and the web 20B of this sole are pivotally connected by vertical axis 27.In this case, can control the also axle of drive installation wheel 21.When axle is not driven, controlled ratch will only allow tamping roller to move along the traffic direction of tractor.May need to increase the weight of lateral chassis frame part 20A in this occasion, to guarantee adequate stability.
When at compacting pattern lower-pilot tamping roller, the aforesaid roll shaft displacement of ramming can take place in described axle.For alleviate this impact displacement in Fig. 8 and 9 connecting rod and heavy chassis and integrally dragging car element 20A and 20B on the stress that produced, axle 25 can be rotated around the front axle and the rear axle of machine.
In the practice, it is favourable that rotatable connection is installed near axle 25, so that the compacts that restriction is quickened around roll shaft.As the following explanation that will carry out in conjunction with Figure 10-14, by around its center axle 25 pivotal mounting can advantageously be realized above-mentioned purpose on chassis and Connection Element, provide limiting its around yawing axis around, the i.e. device of vertical axis motion.
By Fig. 8 and 9 as can be seen, the wheel 21 suitable distances of being separated by, shown in equal the overall width of machine in the situation substantially, this width is formed by the outer rim of compacts 24.With compare in conjunction with the described conventional tamping roller of Fig. 1-3, this can give tamping roller stability and reduce the chance of tamping roller around the roll shaft inordinate rotation.
Referring to Figure 10-14, it shows controllable embodiment of the present invention a kind of practicality, self-propelled.Compactor 30 has been shown in the above-mentioned accompanying drawing, and it comprises the motor chassis frame 31 of a T shape, and this sole is bearing on a pair of ground-engaging wheel 32.Wheel 32 is arranged in each end of lateral shaft (accompanying drawing is not shown), and this axle can drive and can handle, and it is by the lateral part supporting of T shape sole.
Sole 31 also has the 33 pairs of supportings of series connection wheel towards the end of the web part 34 of sole.Shown in Fig. 8 and 9, it is very narrow that sole 31 is designed, and the clear space between the compacts is only sufficient in holding web part and wheel.Equally shown in Fig. 8 and 9, driven, steerable axle adds that total lateral dimension of its wheel that supports 32 is substantially equal to the overall width that is formed by compacts 35.Thereby obtain good anti-stability in roll once again.
Each compacts 35 is three rollers with three circumferentially spaced salient points 36.After each salient point is a recessed portion 37, and is a compaction plane 38 after each recessed portion 37.Compacts is fixedly mounted on the common axis 39 of 40 li on axle box, rams with box lunch and rotates together when roller moves on the ground.
The draw bar 44 of approximate horizontal and vertical links 45 pin joints are on the pivoting point 41 of the rear bulkhead 42 of sole 31.Draw bar 44 and vertical rod 45 can be around pivoting point 41 independent rotation.The upper end pin joint of vertical links 45 is on the axle axle point 46 of the piston rod of hydraulic jack 47.
In order compacts to be promoted to the delivery pattern, to stretch out the jack 69 that has plate 71, plate 71 is hinged below 72 places and draw bar 44.Thereby lift draw bar 44, and take up shaft device and compacts.
The heel pin of hydraulic spring grease cup 47 is connected on the pivoting point 48 of dividing plate 42, and this spring is along the direction work of cardinal principle level.Hydraulic spring grease cup 47 has the punch rod of a hydraulic starting, and it is connected with an air charged accumulator (not shown), so that required load amount of deflection feature to be provided.Vertical links 45 be provided with baffle plate 49 near centerpivot point place, and on dividing plate 42, be fixed with the rubber bumper 50 relative, to form the limit of sports record stop of vertical links 45 with baffle plate 49.
The tail end of draw bar 44 passes through pivoting point 52 pin joints on decline bar 51.The top of decline bar 51 is by the tail end of pivoting point 53 pin joints at isolating bar 54, and the front end of isolating bar 54 passes through pivoting point 55 pin joints on vertical links 45.
Should be pointed out that pivoting point 55 is between pivoting point 41 and 46.The bottom of decline bar 51 is big U-shaped, and it is connected across on the axle box 40, and pivotally connected by a pintle assembly 56 and axle box 40.
Draw bar 44, vertical rod 45, isolating bar 54 and decline bar 51 and relevant pivot and hydraulic spring grease cup 47 thereof are formed connected system together jointly.These connected system restriction axle box 40 relative dividing plates 42 are done forward, motion backward, and can not freely do the clinoid motion, and allow axle box 40 to do upper and lower motion, can be freely around roll shaft, and promptly pivot device 56 rotates.
Should be appreciated that being connected between sole 31 and the compacts 35 is flexible in essence.At work, motor acts on driven shaft 32 with the transmission device that is installed in sole 31 front portions, so that drive forwards machine along direction shown in the arrow among Figure 10 57, simultaneously by elastic connecting system traction compacts 35.Except allowed for common axis 39 the elasticity of torsion allowed slight asynchronous, the compacts of kiss the earth is consistent each other to rotate.
In this rotation of each compacts, it repeats a process, and wherein, compacts rises at salient point 36 places, subsequently in case reach state above the center,, fall forward, then rams ground by compaction plane 38 just downwards.
If compacts 35 is rammed ground boss, during position 13 as shown in Fig. 5 and 6, pintle assembly 56 allows the composite set of two compacts 35, common axis 39 and axle boxes 40 to rotate around the tamping roller roll shaft.This can be avoided producing excessive stress on connected system.In Fig. 6, the average ground of numbering 14 expressions, and also as indicated above, the roll shaft motion that arrow 15 expression compacts are right, one of two compacts impact boss or obstruction 13 at this moment.
Figure 13 and 14 is represented the detailed structure of pintle assembly 56.Tubulose axle box 40 has flat board 59, enters its side forward, backward.The following U-shaped part of decline bar 51 is across the flat part that is formed by plate 59, and it is pivotally connected to pass through pivot pin 60 and axle bush and this plate.At the restriction pad 62 that the end of decline bar drag hook has 4 side direction to separate, it acts on the steel friction plate 58, to stop the axle box assembly around clinoid, promptly rotates relative to sole 31 around vertical axis.Steel friction plate 58 is welded on the plate 59.Can regulate by adjustment screw 63 by the restriction pad 62 that nylon material is made, with compensate for wear.
In order to control speed and the degrees of rotation thereof of axle box 40, provide 2 hydraulic cushion oil cylinders 64 around the roll shaft rotation of the axle of pintle assembly 56.On draw bar 44, and pivoting point 68 pin joints of oil cylinder self by groove is arranged are on axle box 40 by pivoting point 67 pin joints for the piston rod of oil cylinder 64.
Two oil cylinders 64 are connected with air filling type hydraulic accumulator 66 by regulating limiting holes 70, and this hole allows limited hydraulic fluid to flow to accumulator by oil cylinder.
Parallel connected with each adjustable orifice 70 is an one way valve 65, and it can be free movable to oil cylinder 64 by accumulator 66.Under static state, axle box 40 is roughly parallel to draw bar 44, all is the state that stretches out fully owing to the pressure in the accumulator makes the piston rod of cushion cylinder 64.In this state, piston 75 is positioned at its upper limit place in oil cylinder, and pivot pin is positioned at the limit place, bottom that it moves in the groove of pivoting point 68 down.
If the roll shaft displacement of axle box 40 relative draw bar 44 orientations takes place, hydraulic unit is worked as follows.Suppose that right side shown in Figure 13 moves upward.Because the oil cylinder latch has been positioned at the bottom of groove 68, the motion by axle makes oil cylinder 64 begin to move upward.Fluid in the oil cylinder is forced through out the hole of pushing up 75 central authorities at piston.Do not have fluid because seal 75a is arranged and around piston top 75, overflow, the fluid hole 75b that flows through.One way valve 65 is closed, and the hole 70 so that fluid is flowed through, thereby control axle box 40 is around the roll shaft speed of pivot 56.
Consider left hand oil cylinder 64 now, it is static that the oil cylinder latch keeps, and ear on the axle box 40 and groove 68 thereof move downward, and engage with latch up to the upper end of groove, thereby form the limit that allows axle to rotate.Reach the limit of sports record of right hand piston simultaneously.The fluid of discharging from the oil cylinder of right side can not be included the left side oil cylinder in, because it has been full.Therefore, fluid flows into the accumulator 66 that keeps predetermined fluid pressure.In case remove the disturbing moment that acts on the axle box 40, the pressure fluid one way valve 65 of can flowing through without restriction, so that produce a power between right hand piston 75 and oil cylinder 64, it tends to recover the parastate between draw bar and the axle box 40.
From the fluid pressure operated that the continues left side and the right side oil cylinder 64 of accumulator 66, so that between axle box 40 and draw bar 44, form self-centering moment.Can regulate the size of this self-centering moment by handling control valve for fluids 73, or the fluid of 66 li of accumulators is drained into groove 74 with the reduction fluid pressure, or fluid be charged in the accumulator, to improve fluid pressure by pump 80.
By above-mentioned self-centering unit, can make machine with the work of delivery pattern, by compacts restriction roll shaft is at random moved.Suitably speed realizes safe transport between construction ground by this way.
Therefore Figure 10-14 expression is based on of the present invention a kind of embodiment of unitized frame shown in Figure 8 and control system.The following describes a kind of application of the present invention on vehicle frame shown in Figure 9 and control system.
Fig. 9 representation class is similar to vehicle frame shown in Figure 8, but the manipulation of driving wheel is to realize by vertical deflection pivot 27.Therefore, this is a kind of frame system and frame of connection.The frame system and frame that connects is widely used in the machinery that builing industry is used, and adds carrier aircraft and compactor etc. as front end.Except vertical pivot, the standard method of this conventional machine is to allow because the motion of roller slowly that the ground unevenness causes by the roll shaft pivot that the limited angular movement of general permission is provided.In this common connection design, deflection and the roll shaft pivoting point of two parts by combination of machine that each comfortable normal work period is had the stability of overturning or slip resistance analysis links together.But, in the time should connecting control system and be used for tamping roller, the vehicle frame part among Fig. 9 shown in the numbering 20B only when two compacts kiss the earths, just has intrinsic stability against overturning when promptly working under compaction state.When compacts by jack-up so that be bearing in narrow between compacts of among Fig. 9 one or several when taking turns 23, vehicle frame part 20B is unsettled around roll shaft.Therefore, the roll shaft pivot that is used for the connecting-type vehicle frame of binary tamping roller need impose restraining moment, so that the resistance that stable wide wheel base section 20A can provide required opposing part 20B to topple.
When compacts contacts with ground, when promptly being in the compacting pattern, another factor relevant with the operating characteristic of impact compaction machine determined the roll shaft restraining moment to be applied among Fig. 9 on the connector between the vehicle frame part 20A and 20B.
Referring to Fig. 1, suppose the state work of compacts 2 again with kiss the earth.When the compacts assembly passed through salient point b at the volley, it tended to forward, quickens downwards.In the stable motion of operating rate, this forward, downward motion absorbed by the Connection Element between sole and compacts and the shaft assembly 4,5 and 6, seldom or do not have tangible accelerating force to act on the tractor 10.But, at low speed and stopping period, when startup and operation, decline bar 5 can produce the load pulse of impingement baffle a ends.The net result that acts on this load pulse on the connector 9 is the power that produces at that point up or down.The influence of supposing this power is in connection tractor system shown in Figure 9.During moving linearly as shown in Figure 9, the power that acts on the pivot 27 does not produce any motion around pivot 27, because this pivot does not allow any pitch axis to rotate.But, when handling driving wheel and be state 20C shown in the dotted line, the power downward or upward on the pivoting point 27 of acting on has the leverage around a C, is d around the lever length of this pivotal axis.This couple induces " tractor " or chassis portion 20A forward to carry out elevating movement around its wheel.Because the geometry of this pivot system 27, this elevating movement of chassis portion 20A are attended by pitching and the roll shaft motion of frame elements 20B.When two chassis component are not on coarse straight line, also moment loading that can be produced by driven pulley 21 and the brake force similar pitching effect that produces tractor.
Above-mentioned analysis confirms that a tamping roller needs one to connect frame system and frame, so that common vertical axis or yawing axis, jointed shaft to be provided, and extra roll shaft pivot, to realize the motion of roll shaft slowly between the 20A and 20B two parts among Fig. 9.But, for the parts 20B (Fig. 9) that makes machine has stability against overturning under the delivery pattern, roll shaft need overcome the restriction of roll shaft motion freely.But, the roll shaft restriction should be such: the restriction degree can restrict to the moderate moment restriction of machine at delivery pattern lower edge linear running from the slight moment of machine under the compacting pattern, so that the height moment restriction of machine when high-speed cruising or under the delivery pattern.Be in all strength square forward and under the state backward being absorbed in the state of loose sandy soil, muddy state, traction wheel such as wheel or compacts, or be raised under the state of delivery pattern at compacts under the condition that is unfavorable for moving, or any combination of above-mentioned state, need be locked in vertical direction to the connection of roll shaft pivot, with prevent vehicle frame part 20B too topple or part 20A around the rotation of its wheel axis.
Adopted a kind of embodiment of the connection machinery of a roll shaft restriction system to describe below in conjunction with Figure 15-18 pair.
Figure 15 is a width of cloth elevation, for the structure of display device parts, has removed a compacts, and has done broken section.Figure 16 is the sectional plan view of machine among Figure 15.The motor chassis 80 that connects machinery is connected on the traction vehicle frame 81 that comprises a vehicle frame prolongation 84 by the pivot system 86 of approximate vertical, and it is enough narrow, so that can will be in the space between the compacts 85 with one group of wheel 83.Driving wheel 82 is installed on the tractor chassis 80.The manipulation of this machine turns to jack 87 to realize by manipulation.An axle box 89 is arranged between chassis 80 and vehicle frame 81, roll shaft and clinoid pivot and controlling organization wherein are housed.
Pivot 88 be flange and be fixed on the vehicle frame 81 by bolt 90, bolt stretches in the machined holes on the axle box 89 that has gantry post 91 and thrust bearing 92, it acts on the thrust bearing 93 in the cannelure on the fitting face that is positioned at axle box 89.Flange 94 is fixed on the pivot, to fix and thrust bearing is imposed preload.Described flange has crank-pin 95, rotating torque is being applied on the pivot 88 under the effect of a pair of hydraulic jack 96 by it.The internal mechanism (having omitted some details) of axle box 89 for clarity sake, has been shown in Figure 15 and 16.The amplification diagrammatic sketch of its details has been shown in Figure 17 and 18, and it also shows one and disconnects security system.
Figure 17 represents to connect the detailed structure of vehicle frame 81 and the pivot system of axle box 89.Identical in numbering and Figure 15 and 16, but adopted other numbering to show detailed feature.Figure 18 represents the sectional view at Figure 17 center line A-A and B-B place.
Crank-pin 95 is pivotally connected on the piston rod 127 of oil cylinder 96.In each case, the hydraulic operation at 128 places, hole produces a power on piston rod 127, and this power equals the cross section product of piston rod in hydraulic pressure.Therefore, cylinder is extended so that articulated slab 129 is bearing on the stop block 130.Select the length of piston rod 127, so that two pistons extend to the limit place of its motion, vehicle frame 81 and axle box 89 be vertical alignment just in time, and pin 126 is arranged in its corresponding tooth 94 li of flanges.
Suppose that vehicle frame 81 rotates relative to axle box 89 around roll shaft.Flange 94 has crank flange 121, and it forces (hypothesis) left hand piston bar 127 to enter in the cylinder 96 again, by variable restriction valve 131 control cushioning effects are set.On opposite side (right side), crank-pin 95 pulls down piston rod and cylinder, and the upper end of this cylinder that has right side articulated slab 129 is unfettered.Hydraulic pressure in the cylinder of right side tends to make cylinder component to extend to the state that launches fully, and by predetermined torque vehicle frame 81 and axle box 89 is biased into when allowing the radian of motion in this state, is 30 ° in this case.The hydraulic pressure that acts on this system by change can be regulated the pre set force weak point, and can regulate buffering by the setting that changes limiting valve 131.
Consider now such as the hillside fields vehicle frame 81 to be toppled to the situation greater than the radian that allows motion, in mechanism shown in Figure 17 and 18, this radian is 30 °, or is 15 ° in each side of vertical line.Because it is a V-arrangement, pin 126 can overcome the preload that is applied to it by the hydraulic pressure that is applied by hole 132, and deviates from from its tooth.Flange 94 can be independent of the crank flange and is rotated further like this.When having recovered normal orientation, pin 126 is back to again with tooth and aligns, and can be back to its normal position in tooth in the effect downslide of the hydraulic pressure that is provided by hole 132.Hydraulic pressure in the hole 132 can change, so that regulate the preload that is added on the pin 126, and a hydraulic pressure reducing valve can be provided in this loop,, perhaps unnecessary fluid be included in the pressurized hydraulic accumulator so that when pin moves in its cylinder, fluid is drained in the groove.
The another kind of mode of hydraulic actuation pin 126 is to replace with a shear pin, and this pin is not ideal, because the replacement that will shear is difficult in the art.
For tractive force is reached axle 106 from vehicle frame 81, provide a connected system of forming by draw bar 98, decline bar 99 and stiff spring 97.Stiff spring 97 is hydraulic operated, so that how the elongation of piston rod all provides one near stable tractive force.Each end at decline bar 99, buffer board 101 is provided with limit of sports record snubber 100, and it is preferably made by hard rubber.
Realize that by a pivot 102 decline bar 99 rotates relative to the pitch axis of vehicle frame 81, and realize the pitch rotation of draw bar 98 relative decline bars 99 by pivot 103.
Adopt this connected system, the end 104 of draw bar 98 can freely upper and lower, forward and backward motion, but vehicle frame 81 is freely done the roll shaft angular displacement relatively, the following describes thereafter to go on foot.
If the end 104 of draw bar 98 is connected on the axle box 105 admittedly, and any roll shaft displacement of axle box 105 can cause that all vehicle frame 81 moves along with described roll shaft then, and around pivot 88 rotations.
Because vehicle frame 81 is very heavy, has the big moment of inertia around roll shaft, it rotates in time the rotational hysteresis of axle relatively.Therefore, along with the displacement of impact type roller, draw bar 98 can rotate, to attract the lost motion between axle box 105 and the vehicle frame 81.
In the embodiment of the present invention shown in Figure 10-14, adopt identical analysis, but transmission in this case/control type vehicle frame 31 has greater than the quality of vehicle frame part 81 shown in Figure 15 and moment of inertia, because it comprises engine, transmission mechanism and driving wheel.In the embodiment shown in Figure 10-14, pivot 56 permission axles 40 have enough displacements of relative vehicle frame 31, so that its rotation can be subjected to the control of cushion dashpot 64, to avoid that excessive stress is arranged on vehicle frame and Connection Element.
In the embodiment shown in Figure 15-18, because the rotator inertia square of vehicle frame 81 is less than vehicle frame among Figure 10 31 in actual design, usually doubly, can form differential between axle boxes 105 and index bar 104 ends by the rubber element of installing with following method 107 and 108 less than its 2-5.
Figure 19 represents local side-looking, the partial sectional view along the longitudinal midline of machine.Figure 20 represents an end-view, and Figure 21 represents the plan view of axle box 105, and draw bar is removed, with the position and the orientation of expression rubber element 107 and 108.These can resist compression load on its big area for the rubber element of rubber pad form, and slight deflection is only arranged, and are generally 10% of mat thickness.Its lateral dimensions is designed to have the shear deflection that is generally mat thickness 50%.
For the elasticity centerpivot that provides to be used for roll shaft motion, rubber pad 108 is installed on the plate 109 in the draw bar structure, to act on the torsion elements of integrating with axle box 105 110.Figure 21 represent compression pad 108 and shear pad 107 be how mounted in pairs at the either side of axle box.
When jack 111 work, apply a lifting force by compression pad 108 by plate 109 so that lift axle 105 and connected compacts right.By the resistance of shear pad, can carry out any shearing motion simultaneously with compressed format generation traction and stopping power.Roll shaft motion between axle box 105 and the draw bar 104 makes pad 107 distortion with shear pattern, up to limiting its further motion by the limit movement snubber 112 that is attached on the axle box 105.The not obvious restriction of formula crash roll 108 by compression of roll shaft motion allows its motion because it only is deformed into.
For ease of assembling draw bar 104 and axle box 105, will fill up 107 and 108 and be bonded on the axle box structure.Draw bar 104 is installed on the axle box, with restriction pad 108, between shear pad 107 and relative compressive plate 113 gap is arranged.Tighten screw 115 then so that to shear pad 107 preloading, and tighten screw 116, so that to compression pad 108 preloading.
Conventional bindiny mechanism adopts vertical axis pivot system, the only limited freedom around the roll shaft motion.This is that upper links by a weak point realizes that it can be swung to either side in short radian.For above-mentioned reasons, yawing axis not being biased into maintenance vertically just can not be with its Secure Application in tamping roller.
In Figure 22 and 23, vertical or deflection connects axis between upper and lower ball joint 135.The last connecting rod 136 of deflection pivot system also can be rotated in the vehicle frame end by a ball joint 137.Connecting rod 136 can be by applying the longitudinal axis of mode constrained linkage 136 and vehicle frame from hydraulic pressure to plunger 138 be in line, in this case, no roll shaft degree of freedom between vehicle frame 81 and the motor chassis 80.By alleviating two hydraulic pressure on the plunger 138, along with the default side force effect on the connecting rod 136 of pivoting point 137 can be carried out lateral movement.The cylinder of plunger 138 is pivotally connected on the lever arm 139, and when stretching out fully with each plunger rod of box lunch, this lever abuts against on the retainer 140, can regulate the position of this retainer with screw 140A.The control of radial type machinery realizes by handling steering jack 141 among Figure 22 and 23.
Above-mentioned self-propelled impact compaction facility have a lot of key characters, comprising:
1. driven pulley 21,32 and 82 has bigger spacing each other.The wheel stitch width, the no big difference of lateral dimensions between promptly taking turns and taking turns and compacting track (i.e. the lateral width that forms by the compacts outer rim).This makes machine have the remarkable stability that anti-vehicle frame topples, and vehicle frame is on the narrow wheel base between the compacts.This principle also can be applicable on single compacts relative with two compacts machineries.
2. the roll shaft pivot in each embodiment of the invention described above can be done roller displacement slowly, and reduces the potential damaging effect of roll shaft motion, and buffering relevant with roll shaft and self-centering function have adequate stability.In hinged machinery shown in Figure 15-21, the shaft coupling piece between axle box and decline bar can be done roll shaft motion limited, that cushioned, and the motion of potential damaging impact formula roller has considerable influence to the decline bar.The buffering of roll shaft motion can also reduce the possibility of potential nuisance vibration.
3. in embodiment shown in Figure 15-18, constitute the disconnection safety device by locking device, lock 126 and relevant tooth thereof, it can throw off vehicle frame and this mechanical traction element effectively under the condition of the excessive roll shaft motion of vehicle frame.Therefore, if vehicle frame has run into the roll shaft motion that it can be toppled, this motion can not passed to draw-gear.
Claims (20)
1. self-propelled impact compaction machine, it comprises a chassis, a tractor that is contained on the chassis, be contained in the ground-engaging wheel on the chassis, at least some is taken turns by tractor drives, and one or several impact compaction body that is connected with chassis elasticity, described one or several compacts forms the compacting track width, this width is the width from a side of described one or several compacts to another side relative with it, and the maximum that the ground-engaging wheel on chassis forms wheel stitch width and compacting track width and no significant difference, therefore, this chassis has significant roll shaft stability.
2. self-propelled impact compaction machine as claimed in claim 1 is characterized in that it comprises that a pair of elasticity that is bearing in is connected in impact compaction body on the common axis on the chassis, has the ground-engaging wheel on the chassis that is installed between the compacts.
3. self-propelled impact compaction machine as claimed in claim 2, the maximum that it is characterized in that being formed by the ground-engaging wheel on chassis wheel stitch width equals substantially or only is slightly less than by the formed compacting track width of the side direction outer rim of two compacts.
4. as each self-propelled impact compaction machine in claim 2 or 3, it is characterized in that the lifting appliance that it is included on the chassis and works between the compacts, carry so that compacts is lifted on the ground.
5. each self-propelled impact compaction machine as in the above-mentioned claim, the chassis that it is characterized in that this machine is to be formed by single integral rigidity structure.
6. self-propelled impact compaction machine as claimed in claim 5 is characterized in that described driven ground-engaging wheel is the single cardan-shaft suspension by tractor drives.
7. self-propelled impact compaction machine as claimed in claim 6 is characterized in that the axle that supports described one or several compacts has the roll shaft degree of freedom of a spot of relative bobbin movement at least.
8. self-propelled impact compaction machine as claimed in claim 7 is characterized in that it comprises that buffer is to cushion the roll shaft motion on chassis relatively of described axle.
9. as each self-propelled impact compaction machine among the claim 1-4, the chassis that it is characterized in that this machine has by be connected to each other together front and rear of vertical clinoid.
10. self-propelled impact compaction machine as claimed in claim 9 is characterized in that it comprises roll shaft pivot between described front and rear.
11. as the self-propelled impact compaction machine of claim 10, it comprises buffer, so that the roll shaft in buffering front portion, relative chassis, rear portion, chassis in the predetermined slewing area of roll shaft pivot moves at least.
12. as the self-propelled impact compaction machine of claim 11, it is characterized in that it comprises a release mechanism, the roll shaft motion between described forward and backward part makes described rear portion can do undamped the rotation relative to the front portion when surpassing preset limit.
13. as each self-propelled impact compaction machine in the claim 8,11 or 12, it is characterized in that described roll shaft buffer is adjustable, to change resistance to relative roll shaft motion.
14. self-propelled impact compaction machine as claim 13, it is characterized in that under the delivery or Transportation Model of this machine, wherein, the impact compaction body is raised off ground, buffer to the resistance of roll shaft motion greater than the resistance under work or compacting pattern, impact compaction body kiss the earth under this pattern.
15., it is characterized in that described buffer is available manual adjustments as each self-propelled impact compaction body in claim 13 or 14.
16. as each self-propelled impact compaction body in claim 13 or 14, the work that it comprises the control, braking or other system that are used for according to this machine is the device of the described buffer of control automatically.
17. as each self-action impact compaction machine among the claim 9-12, this machine comprises:
A pair of be bearing on the common axis that is connected with chassis elasticity the impact compaction body that separates and
An auxiliary roll shaft pivot that is used to overcome the impact type roller motion of described axle.
18. as the self-propelled impact compaction machine of claim 17, it is characterized in that the junction surface of described auxiliary roll shaft pivot between described axle and Flexible Connector, described Flexible Connector connects described axle and chassis.
19. as the self-propelled impact compaction machine of claim 18, it comprises the device that is used to cushion around described auxiliary roll shaft pivot motion.
20. as the self-propelled impact compaction machine of claim 19, it is characterized in that described buffer comprises the buffer of being made up of rubber or other elastomeric material, this snubber has rotation and buffering effect.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| GB9514583.5 | 1995-07-17 | ||
| GBGB9514583.5A GB9514583D0 (en) | 1995-07-17 | 1995-07-17 | Soil compactor with stabilising wheel system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1195383A true CN1195383A (en) | 1998-10-07 |
| CN1143031C CN1143031C (en) | 2004-03-24 |
Family
ID=10777793
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB961967900A Expired - Fee Related CN1143031C (en) | 1995-07-17 | 1996-07-17 | Soil compactor with stabilising wheel system |
Country Status (9)
| Country | Link |
|---|---|
| EP (1) | EP0839233B1 (en) |
| JP (1) | JP2000501797A (en) |
| CN (1) | CN1143031C (en) |
| AU (1) | AU703060B2 (en) |
| CA (1) | CA2227068C (en) |
| DE (1) | DE69624244T2 (en) |
| GB (1) | GB9514583D0 (en) |
| WO (1) | WO1997004179A1 (en) |
| ZA (1) | ZA966036B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110946042A (en) * | 2019-11-15 | 2020-04-03 | 华艺生态园林股份有限公司 | Self-propelled mutual compensation lawn compactor |
| RU200537U1 (en) * | 2020-06-08 | 2020-10-28 | федеральное государственное бюджетное образовательное учреждение высшего образования "Южно-Российский государственный политехнический университет (НПИ) имени М.И. Платова" | Traction and braking device of the road roller |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO1999060218A1 (en) * | 1998-05-21 | 1999-11-25 | Compaction Technology (Soil) Limited | Soil compaction machine |
| EP1131495B1 (en) | 1998-11-09 | 2004-02-25 | Compaction Technology (Soil) Limited | Compaction roller |
| EP1111134A3 (en) * | 1999-12-22 | 2003-10-01 | Hamm AG | Road roller |
| WO2014162261A1 (en) * | 2013-04-02 | 2014-10-09 | Roger Arnold Stromsoe | A soil compaction system and method |
| EP3247837A2 (en) * | 2015-01-21 | 2017-11-29 | Roger Arnold Stromsoe | An impact compactor, compaction system and a method of obtaining soil strength |
| CA2999808C (en) * | 2015-09-25 | 2019-06-04 | Roger Arnold Stromsoe | Impact compactor |
Family Cites Families (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3477535A (en) * | 1967-03-10 | 1969-11-11 | Case Co J I | Roller attachment for a self-propelled vehicle |
| DE2359375C2 (en) * | 1973-11-28 | 1984-06-14 | South African Inventions Development Corp., Pretoria, Transvaal | Compaction roller with a non-circular roller drum |
| GB1583425A (en) * | 1977-05-25 | 1981-01-28 | South African Inventions | Method of operating a compaction roller assembly and a compaction roller assembly |
| US4422795A (en) * | 1979-04-09 | 1983-12-27 | Berrange Aubrey R | Compactor |
-
1995
- 1995-07-17 GB GBGB9514583.5A patent/GB9514583D0/en active Pending
-
1996
- 1996-07-16 ZA ZA9606036A patent/ZA966036B/en unknown
- 1996-07-17 JP JP9506422A patent/JP2000501797A/en active Pending
- 1996-07-17 EP EP96924977A patent/EP0839233B1/en not_active Expired - Lifetime
- 1996-07-17 WO PCT/GB1996/001708 patent/WO1997004179A1/en active IP Right Grant
- 1996-07-17 DE DE69624244T patent/DE69624244T2/en not_active Expired - Fee Related
- 1996-07-17 CN CNB961967900A patent/CN1143031C/en not_active Expired - Fee Related
- 1996-07-17 CA CA002227068A patent/CA2227068C/en not_active Expired - Fee Related
- 1996-07-17 AU AU65243/96A patent/AU703060B2/en not_active Ceased
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110946042A (en) * | 2019-11-15 | 2020-04-03 | 华艺生态园林股份有限公司 | Self-propelled mutual compensation lawn compactor |
| RU200537U1 (en) * | 2020-06-08 | 2020-10-28 | федеральное государственное бюджетное образовательное учреждение высшего образования "Южно-Российский государственный политехнический университет (НПИ) имени М.И. Платова" | Traction and braking device of the road roller |
Also Published As
| Publication number | Publication date |
|---|---|
| CA2227068C (en) | 2004-09-28 |
| AU703060B2 (en) | 1999-03-11 |
| JP2000501797A (en) | 2000-02-15 |
| DE69624244D1 (en) | 2002-11-14 |
| AU6524396A (en) | 1997-02-18 |
| EP0839233B1 (en) | 2002-10-09 |
| WO1997004179A1 (en) | 1997-02-06 |
| EP0839233A1 (en) | 1998-05-06 |
| CN1143031C (en) | 2004-03-24 |
| DE69624244T2 (en) | 2003-06-18 |
| CA2227068A1 (en) | 1997-02-06 |
| GB9514583D0 (en) | 1995-09-13 |
| ZA966036B (en) | 1998-01-16 |
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