CA2042890A1 - Soil compactor - Google Patents
Soil compactorInfo
- Publication number
- CA2042890A1 CA2042890A1 CA 2042890 CA2042890A CA2042890A1 CA 2042890 A1 CA2042890 A1 CA 2042890A1 CA 2042890 CA2042890 CA 2042890 CA 2042890 A CA2042890 A CA 2042890A CA 2042890 A1 CA2042890 A1 CA 2042890A1
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- CA
- Canada
- Prior art keywords
- subframe
- vehicle
- drum
- drums
- frame
- 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.)
- Abandoned
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Abstract
RBP File No. 5605-003 ABSTRACT OF THE DISCLOSURE
A soil compactor for use in compacting soil or other materials, has full isolation of the operator's station from both front drum vibration and rear road shocks. The compactor contains a front frame articulately joined to a rear frame. The compactor also contains a subframe which supports an operator's station, motive power, and dual fuel/hydraulic oil tank. The subframe is mounted on rubber shocks to the rear frame. The compactor is constructed with a rollover protection structure (ROPS) bolted to the subframe and mounted on isolation mounts to the rear frame. At the rear of the vehicle, a pair of isolation mounts are disposed between the vehicle's dual tank and the rear frame. This structure serves to isolate the operator's station from the drum vibration transmitted through the front frame as well as from the road shock and vibrations transmitted from the rear tires to the rear frame. The soil compactor contains a drum drive consisting of a hydraulic drum motor with splined shaft which is rotatable with the drum hub and a spindle. The spindle is located between the hub and the motor and surrounds the shaft of the motor. Cylindrical roller bearings are placed between the spindle and the hub to permit the hub and motor shaft to rotate with respect to the spindle, and to withstand vibration transmitted by the drums.
A soil compactor for use in compacting soil or other materials, has full isolation of the operator's station from both front drum vibration and rear road shocks. The compactor contains a front frame articulately joined to a rear frame. The compactor also contains a subframe which supports an operator's station, motive power, and dual fuel/hydraulic oil tank. The subframe is mounted on rubber shocks to the rear frame. The compactor is constructed with a rollover protection structure (ROPS) bolted to the subframe and mounted on isolation mounts to the rear frame. At the rear of the vehicle, a pair of isolation mounts are disposed between the vehicle's dual tank and the rear frame. This structure serves to isolate the operator's station from the drum vibration transmitted through the front frame as well as from the road shock and vibrations transmitted from the rear tires to the rear frame. The soil compactor contains a drum drive consisting of a hydraulic drum motor with splined shaft which is rotatable with the drum hub and a spindle. The spindle is located between the hub and the motor and surrounds the shaft of the motor. Cylindrical roller bearings are placed between the spindle and the hub to permit the hub and motor shaft to rotate with respect to the spindle, and to withstand vibration transmitted by the drums.
Description
RBP File No~ 5605-003 Title: Soil Compactor FIE~D OF THE INVENTION
This invention relates to an improved ride-on soil compactor for compacting soil or other materials.
BACRGROUND OF THE INVENTIO~
.
Typical self-propell~ed, ride-on soil compactors contain an operator's station and COllSiSt of a compacting drum or drums located forward of the operator, and rear tires located in the back. The front drum is vibra-ted by a vibration or excita-tion unit. Typically the compactor has a rear frame and a front frame. The use of these vehicles by operators over a period of time has highlighted the problem of operator fatigue and discomfort from ~ibration and shock. The source of these disruptions is twofold: front drum vi~ration transmitted through the front frame and rear tire shocks transmitted through the rear frame.
It has heretofore been known to provide isolation mounts between the vibrating front drums and the rest of the vehicle; however, in that case the operator remains susceptible to road shocks and irregularities transmitted from the rear tires. Isolation o the operator from both the front and rear shocks is particularly important in order to prevent operator weariness which could result in reduced safety and efficiency.
Frequently a soil compactor has a single front drum and a perimeter or front frama to which the frcnt drum is mounted. The presence of a perimeter frame renders the compactor drum incapable of doing work right up to the edge of a trench wall or the like. This is because the perimeter frame protrudes laterally over the drum edge and prevents the drum edge from gaining proximity to the trench wall. The presence of a perimeter frame, moreover, makes it difficult and time-consuming to change the front drum if, for example, it is desired to change from a smooth drum configuration to a padded drum configuration.
More recently soil compactors with dual front drums have been constructed without a perimeter frame.
This construction ensures that the drums can work right up to the trench wall. Also, the compaction width of the soil compactor can be easily varied by merely replacing the drums with drums having a different width. In addition, the absence of a perimeter frame, which provides only static weight, results in greater vibrated mass and in a lower centre of gravity for the vehicle, which improves stability.
Soil compactors typically contain a drum drive consisting of a hydraulic motor which drives the drum. It has also been known to provide an individual hydraulic motor for each rear tire and a main drive consisting of a hydraulic drive unit connected to these individual drive motors.
More recently it has been known that a soil compactor may be provided with an articulated steering mechani~m by providing an articulated joint between the front and rear framss. As a result, the front frame can pivot in both the horizontal and vertical directions relative to the rear frame to provide a more undisturbed finish of the top layer of the material being compacted versus skid steering sys-tems.
This invention relates to an improved ride-on soil compactor for compacting soil or other materials.
BACRGROUND OF THE INVENTIO~
.
Typical self-propell~ed, ride-on soil compactors contain an operator's station and COllSiSt of a compacting drum or drums located forward of the operator, and rear tires located in the back. The front drum is vibra-ted by a vibration or excita-tion unit. Typically the compactor has a rear frame and a front frame. The use of these vehicles by operators over a period of time has highlighted the problem of operator fatigue and discomfort from ~ibration and shock. The source of these disruptions is twofold: front drum vi~ration transmitted through the front frame and rear tire shocks transmitted through the rear frame.
It has heretofore been known to provide isolation mounts between the vibrating front drums and the rest of the vehicle; however, in that case the operator remains susceptible to road shocks and irregularities transmitted from the rear tires. Isolation o the operator from both the front and rear shocks is particularly important in order to prevent operator weariness which could result in reduced safety and efficiency.
Frequently a soil compactor has a single front drum and a perimeter or front frama to which the frcnt drum is mounted. The presence of a perimeter frame renders the compactor drum incapable of doing work right up to the edge of a trench wall or the like. This is because the perimeter frame protrudes laterally over the drum edge and prevents the drum edge from gaining proximity to the trench wall. The presence of a perimeter frame, moreover, makes it difficult and time-consuming to change the front drum if, for example, it is desired to change from a smooth drum configuration to a padded drum configuration.
More recently soil compactors with dual front drums have been constructed without a perimeter frame.
This construction ensures that the drums can work right up to the trench wall. Also, the compaction width of the soil compactor can be easily varied by merely replacing the drums with drums having a different width. In addition, the absence of a perimeter frame, which provides only static weight, results in greater vibrated mass and in a lower centre of gravity for the vehicle, which improves stability.
Soil compactors typically contain a drum drive consisting of a hydraulic motor which drives the drum. It has also been known to provide an individual hydraulic motor for each rear tire and a main drive consisting of a hydraulic drive unit connected to these individual drive motors.
More recently it has been known that a soil compactor may be provided with an articulated steering mechani~m by providing an articulated joint between the front and rear framss. As a result, the front frame can pivot in both the horizontal and vertical directions relative to the rear frame to provide a more undisturbed finish of the top layer of the material being compacted versus skid steering sys-tems.
2~ 9~
There are a variety of means of imparting vibratory motion to the front drums of a soil compactor.
One method is to provide a vibrator mechanism mounted on top of the drums. These type of vibrators or exciters are typically located on the drum frame and provide vibrator motion to both the drum frame and the drums. In these systems, vibratory mo~ion is typically provided by a hydraulic motor which drives a single eccentric weight.
These above-the-drum mounted vibrators have the disadvantage of decreasing the operator~s visibility and have relatively high centres of gravity, which increases instability. Single eccentrics produce centrifugal forces on the drums and result in drum motion in a 360 arc. As a result of this type of motion, the top layer of the material being compacted tends to become disturbed.
It has also been known to provide a vibrator assembly which consists of dual, counter-rotating eccentrics which impart a vertical net force on the drums, as disclosed in U.S. Patent No. 4,927,289. Counter-rotating dual eccentrics produce vertically directedamplitude of the front drums. With vertically directed amplitude systems, higher compaction of the surface of the material being compacted can be achieved. Furthermore, vertically directed amplitude systems result in a greater proportion of mass being vibrated. In addition, the ratio of the centrifugal force of the soil compactor of the invention versus the machine mass is approximately twice as large as for a conventional-soil compactor.
It has also been known to provide for a single drum soil compactor a vibrator assembly which is located inside the drum, see for example, U.S. Patent No.
4,647,247. It has not been shown, however, how to provide such a vibratory assembly inside a dual front drum arrangement. Moreover, the internal vibratory assemblies heretofore ~nown are arranged so-that vibration is applied ~ 3 directly to the drum. This arrangement usually requires that isolation mounts be placed between the perimeter drum frame and the vibrator assembly, causing undue complexity of the vibrator assembly. It is desirable to pro~ide dual counter rotating eccentrics in a vibrator assembly which is located within dual front drums and which is capable of imparting vibration to the drums. It i6 furthermore desirable ~o impart such vibration through the front frame to the drums.
Moreover, it is clesirable to improve the construction costs and compactness of the soil compactors heretofore known. It is desirable to provide a combination fuel and hydraulic oil tank in the soil compactor, thereby reducing construction C09t and wasted space.
SUMNARY OF TE~ INVE~TION
It is therefore an object of this invention to provide an improved dual front drum soil compactor having internal, dual counter-rotating eccentrics which provides full isolation of the operator's station from both road - 20 shocks in the rear and from vibration of the drums. It is desirahle ~hat the compactor be provided with a subframe assembly upon which the motive power, fuel and hydraulic oil tank and operator's station are located.
It is a further objec~ of this invention to provide a soil compactor having an improved drum drive.
It is a further object of this invention to provide a soil compactor having a dual tank which carries both fuel and hydraulic oil.
According to the preferred embodiment of the present invention, there is provided a ride-on soil compactor having twin front drums. The compactor is sel~-propelled and has four hydraulic drives; the main dxive is connected to individual hydraulic motors for each wheel or drum. The soil compactor of the invention provides that the vibrator assembly or exciter unit for the drums consists of twin counter-rotating eccentric weights enclosed within the front drums. The vibrator provides vibration to the front frame of the vehicle which in turn provides vibration to the drllms. There is no direct provision of vibration to the drums. The soil compactor has articulated steering and t~lO pneumatic drive tires at the rear. The rear tires have limited slip which is achieved hydraulically by use of a flow divider. The compactor is designed to function without the use of a perimeter frame on the front drums.
One particularly advantageous feature of the present invention is the provision of full isolation of the operator's station from drum vibration as well as rear shocks and road irregularities. This feature is achieved by mounting the operator's sta~ion on a subframe on rubber shocks. The subframe is mounted to the rear frame by providing two pairs of isolators on the vehicle. This system of full isolation avoids the need to provide direct isolation between the vibratory assembly and the rest of the vehicle.
The soil compactor of this invention contains an improved drum drive consisting of a spindle assembly fitted to the drum hydraulic motor. The spindle assembly contains a spindle fitted to the hub of each drum. The spindle assembly employs a cylindrical roller bearing to withstand drum vibration.
The dual tank contains hydraulic oil in one compartment and fuel in the other. The tank contains a dividing centre wall separating the ~wo compart~ents.
In accordance with one aspect of the present invention, there is provided a vehicle for compactin~ soil or other materials which comprises:
5 a~ a front frame;
b~ at least one compacting drum rotatably mounted on the frame;
c) a rear frame joined to said front frame;
d) a subframe mounted on said rear frame which contains the oper~tor's station for said rear frame; and e) isolation mounting means mounting said subframe to said rear frame.
BRIEI? DESCRIPTION OF l~lE DRAWINGS
For a better understanding o~ the present invention and to show more clearly how it may be carried into effect, reference will now be made, by way of example, to the figures, which show a preferred embodiment of the present invention, and in which - Fig. l is a perspective view of the soil compactor according to the present invention.
~ Fig. 2 is a partly sectional plan view of the front frame and drums of the soil compactor of Fig. 1, with section showing drum motor and spindle assembly.
- Fig. 3 is a partly sectional view of the spindle assembly of the invention.
- Fig. 4 is a partly sectional plan view of the soil compactor front frame and drums of 5Fig. 2 with section showing the vibratory assembly .
- Fig. 5 is a partly sectional side view of the invention, looking in the direction of arrows 5 of Fig. 7.
10- Fig. 6 is a part].~ sectional side view of the invention shown in Fig. 5 with an engine cover assembly opened up, looking in the direction of arrows 6 of Fig. 7.
- Fig. 7 is a partly sectional plan view of the soil compactor of Figs. 5 and 6 with local cutaways.
- Fig. 7A is a side view of the front isolator of the invention looking in the direction of arrow A of Fig. 6.
- Fig. 8 is a partly cutaway explodèd 20perspective view of the front drum assembly showing detail of a hitch assembly.
DESCRIPTION OF TEE PREFERR~D EMBODIN~T
Reference is made first to Fig. 1 which shows a soil compactor 10 according to the invention. The soil compactor 10 is a ride-on motor vehicle consisting of two twin front drums 12 mounted on a front frame 14. The front frame 14 is connected through a hitch (not shown in Fig.
1) to a rear frame 16. The front frame 14 has an aperture 15 disposed near its bottom front edge for towing the vehicle or tying it down on a truck. The rear frame 16 supports a subframe 18 which contains an operator's station 20. ~he rear frame 16 has two rear pneumatic tires 22 mounted on it/ at either side of the vehicle, and supports a dual tank (not shown in Fig. 1) and the motive for power for the vehicle.
The vehicle contains a rollover protection structure (ROPS) 24 consisting of -two ROPS arms 26 along either side of the vehicle. The ROPS arms 26 are joined at their top end to our beams 28 which define a rectangular truss 30. Each of the two vertical ROPS arms 26 are weld~d at their top end to opposing sides of the rear beam 28 below the truss 30. The truss 30 lies in a plane parallel to the ground overhead the operator to protect him from being crushed in the event that the soil compactor 10 rolls over. The ROPS 24 is mounted to the soil compactor 10 at the base o-f each ROPS arm 26 to an outrigger (not shown in Fig. 1). The outrigger extends outwardly o~ the subframe 18 at corresponding locations on the left and right side of the soil compactor 10.
Each front drum 12 consists of a cylindrical roller 34 having a circular drum plate 36 which occludes the interior of the roller 34. The vehicle has individual hydraulic motors for each drum and each tire, as well as a main drive containing a hydraulic drive unit located at the rear of th~ vehicle. The main drive and the hydraulic drive unit are mounted on the subfr~me 18. The drive motors on the various wheels provide motive power to propel the vehicle. The separate hydraulic motors for each drum are conn~cted to the hydrauli drive unit at the rear of the vehicle via respective hydraulic oil hoses (not shown) extending through the gap existing between the front drums 12 and over the front frame 14. The hydraulic connections are achieved by flow dividers to provide a limited slip action for the front drums 12 and for the rear wheels 22.
As best seen in Figs. 2 and 3, each of the front drums 12 contains a drurn drive consisting of a spindle assembly 38, a drum hydraulic motor 40, and a support collar 41 which is mount~d to the front frame 14 of the vehicle. The spindle assembly 38 comprises a hub 42 surrounding a spindle housing or weldment 44. The hub 42 and spindle housing 44 are concentric and have circular cross sections; they conta.in a passa~e disposed through their centres about their centre axes. The spindle housing 44 is fitted to the drive shaft 46 of the drum hydraulic motor 40.
Each spindle housing 4~ has a flange 48 located at its end nearest the drum hydraulic motor 40 and bolted to the hydraulic motor 40. The flange 48 has circumferentially spaced circular apertures S0 near the periphery of the flange 48, parallel to the centre axis of the spindle assembly 38. These apertures 50 are adapted to receive bolts for securing the spindle housing 44 to the support collar 41 for the drum hydraulic motor.
At the other end of the spindle housing 44, opposite from the flange 48 is located a drive plate weldment 52. The drive plate weldment 52 consists of a cylindrical portion 54 welded at its base to a circular plate portion 56. The plate portion has a raised rim 58 at its outer edge which is raised in the direction of the centre of the spindle assembly 38, so that the outer face of the drive plate weldment 52 is flat. The cylindrical portion 54 contains a series of constrictions at its base near the plate portion 56, so that its cross-sectional diameter varies along that section. This permits appropriate annular weld beads to be foxmed, securing the plate portion 56 to the cylindrical portion 54. A series of circumferentially spaced apertures 60 are disposed in the rim 58 parallel to the centre axis o the spindle assembly 38. These apertures 60 are adapted to receive bolts 62 in bores 64. The drive plate weldment 5~ is bolted to the hub 42 by the bolts 62. The edge of the S spindle housing 44 near the drive plate weldment 52 is in close relation to, but spaced from, the drive plate weldment 52.
The drum hydraulic support collar 41 is bolted to the flange 48 with the support collar 41 extending behind the flange 48, and with the motor drive shaft 46 extending forward of the flange 48 through the cenkre of the spindle assembly 38.
The hub 42 suxrounds the outer wall of the spindle housing 44 in the section between the flange 48 and the drive plate weldment 52. The hub 42 is encircled by a hub weldment 63 which i6 a thin member of circular cross-section welded to the hub 42. The hub weldment 63 is spaced from the drive plate weldment 52. It contains a series of equally circumferentially spaced circular apertures 66 which are adapted to receive nuts and bolts to secure the hub 42 to the drum plate 36 at corresponding locations at the edge of the plate 36. Hexagonal bolts are welded in these apertures 66, to facilitate mounting of drums. This further enables different types and sizes of drums to be fitted quickly.
The hub 42 contains a series of steppPd down shoulders 73 along it internal face. Disposed in between the hub 42 and the spindle housing 44 are a pair of cylindrical roller bearings 74. The first roller bearing 74 is located adjacent the neck of the flange 48 and a shoulder 73 of the hub 42. The second bearing 74 is located at the opposite end of the hub 42 against ano~her shoulder 73 near the drive plate weldment 52. The roller bearings 74 are press fit betwe~n the hub 42 and the spindle housing 44. B~tween the two cylindrical roller bearings 74 are placed two bearing spacers 76. The bearing spacer 76 is a cylindrical, thin-walled member having a circular centre bore and a shoulder stepped down from the main body of the spacer 76. The two facing shoulders of the bearing spacers 76 define a notch. The spacers 76 locate and separate the cylindrical roller bearings 74.
Be~ween the bearing spacers 76, at the centre notch thereof, is positioned a thrust plate 78 sandwiched between two thrust washers 80 1o enable the hub to accept radial and axial loads. The thrust plate 78 is a circular, thin, disc-shaped member having a large centre bore and three equally spaced circular holes through its face.
Grease flow emanating from the center of the spindle assembly 38 from a grease fitting 79 located in the center of the drive plate weldment 52 flows through the hole in the thrust plate 78. An O-ring 79 surrounds the cylindrical portion 54 to force grease to flow through the passage between the spindle housing 44 and the cylindrical portion 54. An aperture 81 disposed through the spindle housing 44 permits flow of grease above the thrust washers 80 and into the holes in the thrust plate ~8. The thrust plate 78 is a heavy press fit in the hub 42 so as to form a single unit. The thrust washers 80 are circular, disc-shaped members having a large centre bore and preferablyare made of Delrin TM nylon. A bearing lock nut 82 is fastened to the spindle housing 44 at its extreme end (near the drive plate weldment 52) against the second roller bearing 74. An oil seal and face seal (not shown) encircle the spindle housing 44 and hub 42, respectively at the edge of the hub 42 near the flange 48.
The cylindrical portion 54 of the drive plate weldment 52 ex~ends into the passage of the spindle assembly 38. The cylindrical portion 54 surrounds a spline adaptor 86 extending from an annular step 84 of ~he shaft 2~a~2~9~
46. Nhen the motor 40 is engaged, the hub 42 and drive plate weldment 52 rotate, and the spindle housing 44 remains stationary. The hub 42 bears radial loads only (not axial loads). Thus, the bearings 74 thrust washers 80, thrust plate 78 and bearing lock nut 82 maintain the hub 42 in position relative to the spindle housing 44. ~he shoulder 73 of the hub 42 and the pressure fit of the thrust plate 78 protect the hub 42 and spindle housing 44 from relative motion upon the ~pplication of axial forces to the hub 42.
As best shown in Fig. 5l each drum roller 34 is associated with a drum scraper 88 mounted onto both sides of the front frame 14 of the soil compactor 10. The scraper 88 cons.ists of an upper blade 90 integrally formed with a lower blade 92. The scraper blades 90, 92 are rectangular and extend across the width of the roller 34 and a short distance in the axial direction. Scraper mounting brackets 94 are also integrally formed with the blades 90, 92 and mount the blades 90, 92.
The scraper blades 90, 92 form a "V". The mou~h of the "V" is positioned adjacent the outer surface of the drum roller 34~ ~he scraper 88 serves in known manner to block and dislodge mud etc. which adheres to the roller 34 and rotates past the scraper 88 for rotation of the roller 34 in both directions.
As best shown in Fig. 4, the soil compactor 10 contains a vibratory assembly 96 located within the front drums 12. The vibratory assembly 96 is enclosed within a vibrator housing 98 having a top wall and two side walls.
The vibratory assembly 96 is located above the drum hydraulic motors 40 and spindle assemblies 38~
The vibratory assembly 96 consists of a vibrator hydraulic motor lO0 which drives two vibrator shafts 102.
Each vibrator shaft 102 supports an eccentric weig~t 10 radially extending from the outside wall of the shaft 102 lengthwise along the shaft 102. The two weights 104 are located a~ opposite sides relative to each shaf~ 102 and they would hang down when the vibratory assembly 96 is at rest. The two weights 104 rotate in counter directions to produce vertically directed vibration which is transmitted to the front frame 14. ~he vibratory motion is then transmitted through the hydraulic motor support collar 41l flanges 48 and bearings 74 to the hubs 42 and hellce to the hub weldments 63 and drums 12. The absence of a perimeter frame about the front drums 12 gives the maximum vibrated mass. The vibrator hydraulic motor 100 driv~s the two shafts 102 by means of a drive shaft 106, drive sprocket 108 and drive chain 110 in known manner. The shafts 102 extend between ~wo opposing walls of the vibrator housing 98, parallel to -the drum axes, their ends journalled in bearings 112. The shafts 102 and bearings 112 are supported by two circular bearing housings 114 bolted to corresponding locations in the side walls of the vibrator housing 98.
As best shown in Figs. 5, 6, 7 and 7a, the soil compactor 10 of the present invention preferably achieves ull isolation of the operator~s station 20 from both front drum vibration and rear wheel shocks and road irregularities by providing both a first isolator 116 and a second isolator 118 symmetrically on both left and right hand sides of the vehicle rear frame 16. On each side, the first isolator 116 is placed in front of the rear tire 22, and the second isolator is placed near the back of the rear tire 22.
The ~irst isolator 116, i5 protected in a shroud comprising first and second parallel plates 120. These plates 120 have corresponding slots 121 and they are mounted along one of their edges in overlapping positions 3~
to the rear frame 16 of the soil compactor 10. They are bolted together by a pair of bolts, one through each outer corner of the plates 120, inserted through a pair of support tubes. The ROPS arm 26 passes -through the corresponding slots in these plates below the point at which the ROPS arm 26 is mounted to an outrigger 122 located on the subframe :L8. The first isolator 116 is enclosed within the space formed by the two parallel plates 120. The ROPS arm 26 is bolted to the outrigger 122 by means of a plate 123 disposed between the outrigger 122 and the ROPS arm 26. A similar plate 123 is bolted to the subframe 18 at the other end of the outrigger 122. Each ROPS arm 26 is also mounted to the rear frame 16 of the vehicle via the isolator 116 as described more fully below.
As best seen in Fig. 7a, the first isolator 116 consists of an inner isolator plate 124 and an outer isolator plate 126. These plates 124, 126 are parallel to and spaced apart from each other and lie in planes perpendicular to the first and second parallel plates 120 and parallel to the plane of the ROPS arm 26. The ROPS arm 26 is bolted to and bisects the outer isolator plate 126.
The inner isolator plate 124 is spaced from the ROPS arm 26 and is joined at its top and bottom edges to the parallel plates 120 which thus additionally serves as a mount for the first isolator 116. A ROPS block 127 is placed at each of the upper and lower edges of the inner isolator plate 124 between the inner isolator plate 124 and rear frame 16 ad~acent each of the two parallel plates 120. Vertical and horizonal bolts secure the rear frame 16 and parallel plate 120 to the ROPS block 127.
The outer isolator plate 126 is bolted to the inner face of the ROPS arm 26. The two isolator plates 124, 126 are generally perpendicular to the two parallel platas 120. A rubber shock absorber 128 flexibly connects 8~3~
the two isolator plates 124, 126 so that they can move relative to one another either vertically or horizontally.
This structure limits the travel of the subframe 18 relative to the rear frame 16 as, for example, when the vehicle is lifted off the ground via the ROPS 24.
In the preferred embodiment of this invention, the ROPS arm 26 is slanted downwardly toward the front of the vehicle, and is not perpendicular to the ground.
Preferably the inner and outer isolator plates 124, 126 are thus also tilted slightly with respect to the ground.
It can be appreciated that a variety of positions for the isolator plates 124, 1~6 are possible depending upon the precise structure of the ROPS arm.
As best seen in ~ig. 7 the second isolator 118 has a structure substantially the same as the first isolator 116. Reference numerals with the suffix "a"
indicate corresponding parts. The second isolator 118, however, is located to the rear of the first isolator 116, inwards of the rear frame 16. The two isolator plates 124a, 126a are again parallel spaced plates flexibly connected by a rubber shock absorber 128a . The outer isolator plate 125a is bolted to the rear frame 16 as shown in FigsO 5 and 6. As best seen in Fig. 7, the other, inner isolator plate 124a lies within the rear frame 16 spaced from the outer isolator plate 126a. The inner isolator plate 124a is joined at one edge to the front wall panel 130 of the tank 132 of the vehicle. The two isolator plates 124a, 126a can move relative to one another either vertically or ho~izontally. A shrouding 134 protects the isolator 118. An identical second isolator 118 is disposed in a corresponding position on the right hand side of the vehicle, and the shrouding is shown removed on the left hand side.
As best seen in Fig. 6, the operator's station ~o~ r3 20 of the soil compactor 10 contains a rubber bumper 136 mounted at the base of the station 20. The engine cover 138 of the vehicle is integral with the operator's station 20 and, can be lifted up by means of a hinge located at the back of the vehicle. The rubber bumper 136 rests on an operators platform foot plate 137 when the engine cover 138 is closed. The rubber bumper 136 absorbs vibrations to protect the operator's station 20 fxom road shock and irregularities transmitted through the rear frame 16.
As best seen in Fig. 5, the drum plate 36 contains a cover plate 140 fastened thereto. The cover plate comprises a generally rectangular metal sheet having a perforations (not shown) at either side of its bottom edge and having a rounded top edge. The perforations enable the coverplate 140 to be secured to the drum plate 36 by means of bolts 142 and corresponding perforations (not shown) in the drum plate 36. The cover plate 140 provides a mechanism to check the hydraulic oil level in the vibratory assembly 96.
As best seen in Figs. 5 and 7, the tank 132 is a dual hydraulic oil and fuel tank of generally rectangular shape. It contains a rear panel 144 which slopes downward toward the vehicle a~ its base. ~he tank 132 also has a top wall panel 146, two side wall panels 148 and a front wall panel 130. A divider plate 150 bisects the tank 132 across its cen~re extending between the front wall panel 130 and rear wall panel 144 from top to bottom of the tank. The divider plate 150 serves to separate the fuel subtank 152 of the tank 132 (located on the right side of the vehicle) from the hydraulic oil subtank 154 of the tank 132 (located on the left side of the vehicle).
Each subtank contains a s~iffener arm 156 which extends between opposing front 130 and rear walls 144 of the tAnk 132 whilst permitting free flow of oil hetween the two parts of each tank. The hydraulic oil subtank 154 contains a baffle 158 which extends from the front wall panel 130 of that subtank 154. The baffle 158 is substantially straight near the front wall pan~l 130 and slants toward the left side wall panel as it extends closer to the rear wal] panel 144. The baffle 158 blocks returning oil from mixing directly wikh e~iting oil. The hydraulic oil subtank 154 also contains an elbow 160 having an internal passage. The elbow 160 is located below the baffle 158 and extends from the front wall panel 130 and curves toward the left side wall panel of the vehicle. The elbow 160 connects with a hydraulic supply hose (not shown) through which hydraulic oil exits the hydraulic oil subtank 154. The elbow 160 contains a hydraulic screen (not shown) disposed in its passage to filter the oil.
The hydraulic oil subtank 154 contains a hydraulic oil filler hole 162 disposed in the top wall panel 146 of the tank 132. It also contains a coupling 164 in the top wall panel 146 where hydraulic oil returns from the vibratory circuit. Another coupling (not shown) is located in the front wall panel 130 through which hydraulic oil returning from the cooling circuit passes.
The fuel subtank 152 contains a fuel filler hole 166 for entering fuel which is disposed in the top wall panel 146 of the tank. The fuel subtank 152 contains a fuel sender 168 disposed in the top wall panel 146 for gauging the fuel levelO
As best shown in Figs. 5, 7 and 8, the preferred embodiment of the soil compactor 10 of the in~ention contains a steering arm 170 rotatably connected at one end to the rear frame 16. The forward end of the arm 170 terminates at the hitch 172 of the soil compactor 10. The 2~ 85~
- 1~
hitch 172 consists of a barrel 174 welded to the rear most end of the front frame 14. The barrel 174 opening faces the rear of the vehicle, with the its centre axis lying in the plane of the front frame 14. A port.ion of the front frame 14 extends above and below the barrel 174 and behind the barrel 174 leaving a gap 1.76 between the base of the barrel 174 and the front fra~e 14, as seen in Fig. 5.
As best seen in Fig. 8, the hitch 172 also comprises a shaft 176 mounted on a steering joint 178 by means of a steering hitch weldment plate 180 affixed to the outer surface of the steering joint 178 and facing the barrel 174. The steering joint 178 is a cylinder disposed in an upright position which has a passageway (not shown) disposed through it. The bottom of the steering ~oint 178 abuts the front edge of the rear frame 16. The top o the steering joint 178 abuts an articulation plate 182, which is secured to the rear frame 16. A rotatable articulation pin 186 is disposed through the vertical pin keeper 184 articulation plate 182, steering joint 178 and front edge of the rear frame 16. The articulation pin 186 is journalled in a bearing (not shown) at each of its end~.
Above the articulation plate 182 and lying flat upon it is a vertical pin keeper 184. The vertical pin keeper 184 is joined to the articulation plate 182 and rear frame 16 by means of a bolt located behind the steering joint 178. The pin keeper 184 is able to keep the articulation pin 186 from rotating. The articulation plate 18Z and rear frame 16 have apertures which correspond with the passageway in the steering joint 178.
The steering arm 170 is attached at its forward end in a bracket 188. The bracket 188 is a thin, generally rectangular member ha~ing two opposing rounded faces at the front end of the bracket 188 with corresponding holes extending through the thickness ~he two faces. There is a gap between the faces, so that an attachment member 190 welded to and extending outwardly from the side of the steering joint 178 fits in the gap.
The attachment member 190 has a circular hole corresponding to the hole in the bracket 188. A pin 192 is mounted upright through the bracket 188 and attachment member 190. Two washers 194 are placed fl.at at either end of the pin 192 on the Ou~Qr faces of the bracket 188. This arrangement permits the steering arm 170 to pivot about the head of the bracket 188.
The articulated steering mechanism just described gives a better surface finish, as compared to skid steer compactors. This latter type of compactor tends to disrupt the surface when steeringl which is not the case here.
The preferred embodiment of this in~ention thus achieves the objective of providing full isolation from both front drum and rear wheel vibration by the combination of a operator's station having a rubber shock absorber at its base, and a rear frame mounted to the subframe by rubber isolation mounts. It can be appreciated that a variety of elastomeric mat~rials and means of connection can be provided for said isolators~
There are a variety of means of imparting vibratory motion to the front drums of a soil compactor.
One method is to provide a vibrator mechanism mounted on top of the drums. These type of vibrators or exciters are typically located on the drum frame and provide vibrator motion to both the drum frame and the drums. In these systems, vibratory mo~ion is typically provided by a hydraulic motor which drives a single eccentric weight.
These above-the-drum mounted vibrators have the disadvantage of decreasing the operator~s visibility and have relatively high centres of gravity, which increases instability. Single eccentrics produce centrifugal forces on the drums and result in drum motion in a 360 arc. As a result of this type of motion, the top layer of the material being compacted tends to become disturbed.
It has also been known to provide a vibrator assembly which consists of dual, counter-rotating eccentrics which impart a vertical net force on the drums, as disclosed in U.S. Patent No. 4,927,289. Counter-rotating dual eccentrics produce vertically directedamplitude of the front drums. With vertically directed amplitude systems, higher compaction of the surface of the material being compacted can be achieved. Furthermore, vertically directed amplitude systems result in a greater proportion of mass being vibrated. In addition, the ratio of the centrifugal force of the soil compactor of the invention versus the machine mass is approximately twice as large as for a conventional-soil compactor.
It has also been known to provide for a single drum soil compactor a vibrator assembly which is located inside the drum, see for example, U.S. Patent No.
4,647,247. It has not been shown, however, how to provide such a vibratory assembly inside a dual front drum arrangement. Moreover, the internal vibratory assemblies heretofore ~nown are arranged so-that vibration is applied ~ 3 directly to the drum. This arrangement usually requires that isolation mounts be placed between the perimeter drum frame and the vibrator assembly, causing undue complexity of the vibrator assembly. It is desirable to pro~ide dual counter rotating eccentrics in a vibrator assembly which is located within dual front drums and which is capable of imparting vibration to the drums. It i6 furthermore desirable ~o impart such vibration through the front frame to the drums.
Moreover, it is clesirable to improve the construction costs and compactness of the soil compactors heretofore known. It is desirable to provide a combination fuel and hydraulic oil tank in the soil compactor, thereby reducing construction C09t and wasted space.
SUMNARY OF TE~ INVE~TION
It is therefore an object of this invention to provide an improved dual front drum soil compactor having internal, dual counter-rotating eccentrics which provides full isolation of the operator's station from both road - 20 shocks in the rear and from vibration of the drums. It is desirahle ~hat the compactor be provided with a subframe assembly upon which the motive power, fuel and hydraulic oil tank and operator's station are located.
It is a further objec~ of this invention to provide a soil compactor having an improved drum drive.
It is a further object of this invention to provide a soil compactor having a dual tank which carries both fuel and hydraulic oil.
According to the preferred embodiment of the present invention, there is provided a ride-on soil compactor having twin front drums. The compactor is sel~-propelled and has four hydraulic drives; the main dxive is connected to individual hydraulic motors for each wheel or drum. The soil compactor of the invention provides that the vibrator assembly or exciter unit for the drums consists of twin counter-rotating eccentric weights enclosed within the front drums. The vibrator provides vibration to the front frame of the vehicle which in turn provides vibration to the drllms. There is no direct provision of vibration to the drums. The soil compactor has articulated steering and t~lO pneumatic drive tires at the rear. The rear tires have limited slip which is achieved hydraulically by use of a flow divider. The compactor is designed to function without the use of a perimeter frame on the front drums.
One particularly advantageous feature of the present invention is the provision of full isolation of the operator's station from drum vibration as well as rear shocks and road irregularities. This feature is achieved by mounting the operator's sta~ion on a subframe on rubber shocks. The subframe is mounted to the rear frame by providing two pairs of isolators on the vehicle. This system of full isolation avoids the need to provide direct isolation between the vibratory assembly and the rest of the vehicle.
The soil compactor of this invention contains an improved drum drive consisting of a spindle assembly fitted to the drum hydraulic motor. The spindle assembly contains a spindle fitted to the hub of each drum. The spindle assembly employs a cylindrical roller bearing to withstand drum vibration.
The dual tank contains hydraulic oil in one compartment and fuel in the other. The tank contains a dividing centre wall separating the ~wo compart~ents.
In accordance with one aspect of the present invention, there is provided a vehicle for compactin~ soil or other materials which comprises:
5 a~ a front frame;
b~ at least one compacting drum rotatably mounted on the frame;
c) a rear frame joined to said front frame;
d) a subframe mounted on said rear frame which contains the oper~tor's station for said rear frame; and e) isolation mounting means mounting said subframe to said rear frame.
BRIEI? DESCRIPTION OF l~lE DRAWINGS
For a better understanding o~ the present invention and to show more clearly how it may be carried into effect, reference will now be made, by way of example, to the figures, which show a preferred embodiment of the present invention, and in which - Fig. l is a perspective view of the soil compactor according to the present invention.
~ Fig. 2 is a partly sectional plan view of the front frame and drums of the soil compactor of Fig. 1, with section showing drum motor and spindle assembly.
- Fig. 3 is a partly sectional view of the spindle assembly of the invention.
- Fig. 4 is a partly sectional plan view of the soil compactor front frame and drums of 5Fig. 2 with section showing the vibratory assembly .
- Fig. 5 is a partly sectional side view of the invention, looking in the direction of arrows 5 of Fig. 7.
10- Fig. 6 is a part].~ sectional side view of the invention shown in Fig. 5 with an engine cover assembly opened up, looking in the direction of arrows 6 of Fig. 7.
- Fig. 7 is a partly sectional plan view of the soil compactor of Figs. 5 and 6 with local cutaways.
- Fig. 7A is a side view of the front isolator of the invention looking in the direction of arrow A of Fig. 6.
- Fig. 8 is a partly cutaway explodèd 20perspective view of the front drum assembly showing detail of a hitch assembly.
DESCRIPTION OF TEE PREFERR~D EMBODIN~T
Reference is made first to Fig. 1 which shows a soil compactor 10 according to the invention. The soil compactor 10 is a ride-on motor vehicle consisting of two twin front drums 12 mounted on a front frame 14. The front frame 14 is connected through a hitch (not shown in Fig.
1) to a rear frame 16. The front frame 14 has an aperture 15 disposed near its bottom front edge for towing the vehicle or tying it down on a truck. The rear frame 16 supports a subframe 18 which contains an operator's station 20. ~he rear frame 16 has two rear pneumatic tires 22 mounted on it/ at either side of the vehicle, and supports a dual tank (not shown in Fig. 1) and the motive for power for the vehicle.
The vehicle contains a rollover protection structure (ROPS) 24 consisting of -two ROPS arms 26 along either side of the vehicle. The ROPS arms 26 are joined at their top end to our beams 28 which define a rectangular truss 30. Each of the two vertical ROPS arms 26 are weld~d at their top end to opposing sides of the rear beam 28 below the truss 30. The truss 30 lies in a plane parallel to the ground overhead the operator to protect him from being crushed in the event that the soil compactor 10 rolls over. The ROPS 24 is mounted to the soil compactor 10 at the base o-f each ROPS arm 26 to an outrigger (not shown in Fig. 1). The outrigger extends outwardly o~ the subframe 18 at corresponding locations on the left and right side of the soil compactor 10.
Each front drum 12 consists of a cylindrical roller 34 having a circular drum plate 36 which occludes the interior of the roller 34. The vehicle has individual hydraulic motors for each drum and each tire, as well as a main drive containing a hydraulic drive unit located at the rear of th~ vehicle. The main drive and the hydraulic drive unit are mounted on the subfr~me 18. The drive motors on the various wheels provide motive power to propel the vehicle. The separate hydraulic motors for each drum are conn~cted to the hydrauli drive unit at the rear of the vehicle via respective hydraulic oil hoses (not shown) extending through the gap existing between the front drums 12 and over the front frame 14. The hydraulic connections are achieved by flow dividers to provide a limited slip action for the front drums 12 and for the rear wheels 22.
As best seen in Figs. 2 and 3, each of the front drums 12 contains a drurn drive consisting of a spindle assembly 38, a drum hydraulic motor 40, and a support collar 41 which is mount~d to the front frame 14 of the vehicle. The spindle assembly 38 comprises a hub 42 surrounding a spindle housing or weldment 44. The hub 42 and spindle housing 44 are concentric and have circular cross sections; they conta.in a passa~e disposed through their centres about their centre axes. The spindle housing 44 is fitted to the drive shaft 46 of the drum hydraulic motor 40.
Each spindle housing 4~ has a flange 48 located at its end nearest the drum hydraulic motor 40 and bolted to the hydraulic motor 40. The flange 48 has circumferentially spaced circular apertures S0 near the periphery of the flange 48, parallel to the centre axis of the spindle assembly 38. These apertures 50 are adapted to receive bolts for securing the spindle housing 44 to the support collar 41 for the drum hydraulic motor.
At the other end of the spindle housing 44, opposite from the flange 48 is located a drive plate weldment 52. The drive plate weldment 52 consists of a cylindrical portion 54 welded at its base to a circular plate portion 56. The plate portion has a raised rim 58 at its outer edge which is raised in the direction of the centre of the spindle assembly 38, so that the outer face of the drive plate weldment 52 is flat. The cylindrical portion 54 contains a series of constrictions at its base near the plate portion 56, so that its cross-sectional diameter varies along that section. This permits appropriate annular weld beads to be foxmed, securing the plate portion 56 to the cylindrical portion 54. A series of circumferentially spaced apertures 60 are disposed in the rim 58 parallel to the centre axis o the spindle assembly 38. These apertures 60 are adapted to receive bolts 62 in bores 64. The drive plate weldment 5~ is bolted to the hub 42 by the bolts 62. The edge of the S spindle housing 44 near the drive plate weldment 52 is in close relation to, but spaced from, the drive plate weldment 52.
The drum hydraulic support collar 41 is bolted to the flange 48 with the support collar 41 extending behind the flange 48, and with the motor drive shaft 46 extending forward of the flange 48 through the cenkre of the spindle assembly 38.
The hub 42 suxrounds the outer wall of the spindle housing 44 in the section between the flange 48 and the drive plate weldment 52. The hub 42 is encircled by a hub weldment 63 which i6 a thin member of circular cross-section welded to the hub 42. The hub weldment 63 is spaced from the drive plate weldment 52. It contains a series of equally circumferentially spaced circular apertures 66 which are adapted to receive nuts and bolts to secure the hub 42 to the drum plate 36 at corresponding locations at the edge of the plate 36. Hexagonal bolts are welded in these apertures 66, to facilitate mounting of drums. This further enables different types and sizes of drums to be fitted quickly.
The hub 42 contains a series of steppPd down shoulders 73 along it internal face. Disposed in between the hub 42 and the spindle housing 44 are a pair of cylindrical roller bearings 74. The first roller bearing 74 is located adjacent the neck of the flange 48 and a shoulder 73 of the hub 42. The second bearing 74 is located at the opposite end of the hub 42 against ano~her shoulder 73 near the drive plate weldment 52. The roller bearings 74 are press fit betwe~n the hub 42 and the spindle housing 44. B~tween the two cylindrical roller bearings 74 are placed two bearing spacers 76. The bearing spacer 76 is a cylindrical, thin-walled member having a circular centre bore and a shoulder stepped down from the main body of the spacer 76. The two facing shoulders of the bearing spacers 76 define a notch. The spacers 76 locate and separate the cylindrical roller bearings 74.
Be~ween the bearing spacers 76, at the centre notch thereof, is positioned a thrust plate 78 sandwiched between two thrust washers 80 1o enable the hub to accept radial and axial loads. The thrust plate 78 is a circular, thin, disc-shaped member having a large centre bore and three equally spaced circular holes through its face.
Grease flow emanating from the center of the spindle assembly 38 from a grease fitting 79 located in the center of the drive plate weldment 52 flows through the hole in the thrust plate 78. An O-ring 79 surrounds the cylindrical portion 54 to force grease to flow through the passage between the spindle housing 44 and the cylindrical portion 54. An aperture 81 disposed through the spindle housing 44 permits flow of grease above the thrust washers 80 and into the holes in the thrust plate ~8. The thrust plate 78 is a heavy press fit in the hub 42 so as to form a single unit. The thrust washers 80 are circular, disc-shaped members having a large centre bore and preferablyare made of Delrin TM nylon. A bearing lock nut 82 is fastened to the spindle housing 44 at its extreme end (near the drive plate weldment 52) against the second roller bearing 74. An oil seal and face seal (not shown) encircle the spindle housing 44 and hub 42, respectively at the edge of the hub 42 near the flange 48.
The cylindrical portion 54 of the drive plate weldment 52 ex~ends into the passage of the spindle assembly 38. The cylindrical portion 54 surrounds a spline adaptor 86 extending from an annular step 84 of ~he shaft 2~a~2~9~
46. Nhen the motor 40 is engaged, the hub 42 and drive plate weldment 52 rotate, and the spindle housing 44 remains stationary. The hub 42 bears radial loads only (not axial loads). Thus, the bearings 74 thrust washers 80, thrust plate 78 and bearing lock nut 82 maintain the hub 42 in position relative to the spindle housing 44. ~he shoulder 73 of the hub 42 and the pressure fit of the thrust plate 78 protect the hub 42 and spindle housing 44 from relative motion upon the ~pplication of axial forces to the hub 42.
As best shown in Fig. 5l each drum roller 34 is associated with a drum scraper 88 mounted onto both sides of the front frame 14 of the soil compactor 10. The scraper 88 cons.ists of an upper blade 90 integrally formed with a lower blade 92. The scraper blades 90, 92 are rectangular and extend across the width of the roller 34 and a short distance in the axial direction. Scraper mounting brackets 94 are also integrally formed with the blades 90, 92 and mount the blades 90, 92.
The scraper blades 90, 92 form a "V". The mou~h of the "V" is positioned adjacent the outer surface of the drum roller 34~ ~he scraper 88 serves in known manner to block and dislodge mud etc. which adheres to the roller 34 and rotates past the scraper 88 for rotation of the roller 34 in both directions.
As best shown in Fig. 4, the soil compactor 10 contains a vibratory assembly 96 located within the front drums 12. The vibratory assembly 96 is enclosed within a vibrator housing 98 having a top wall and two side walls.
The vibratory assembly 96 is located above the drum hydraulic motors 40 and spindle assemblies 38~
The vibratory assembly 96 consists of a vibrator hydraulic motor lO0 which drives two vibrator shafts 102.
Each vibrator shaft 102 supports an eccentric weig~t 10 radially extending from the outside wall of the shaft 102 lengthwise along the shaft 102. The two weights 104 are located a~ opposite sides relative to each shaf~ 102 and they would hang down when the vibratory assembly 96 is at rest. The two weights 104 rotate in counter directions to produce vertically directed vibration which is transmitted to the front frame 14. ~he vibratory motion is then transmitted through the hydraulic motor support collar 41l flanges 48 and bearings 74 to the hubs 42 and hellce to the hub weldments 63 and drums 12. The absence of a perimeter frame about the front drums 12 gives the maximum vibrated mass. The vibrator hydraulic motor 100 driv~s the two shafts 102 by means of a drive shaft 106, drive sprocket 108 and drive chain 110 in known manner. The shafts 102 extend between ~wo opposing walls of the vibrator housing 98, parallel to -the drum axes, their ends journalled in bearings 112. The shafts 102 and bearings 112 are supported by two circular bearing housings 114 bolted to corresponding locations in the side walls of the vibrator housing 98.
As best shown in Figs. 5, 6, 7 and 7a, the soil compactor 10 of the present invention preferably achieves ull isolation of the operator~s station 20 from both front drum vibration and rear wheel shocks and road irregularities by providing both a first isolator 116 and a second isolator 118 symmetrically on both left and right hand sides of the vehicle rear frame 16. On each side, the first isolator 116 is placed in front of the rear tire 22, and the second isolator is placed near the back of the rear tire 22.
The ~irst isolator 116, i5 protected in a shroud comprising first and second parallel plates 120. These plates 120 have corresponding slots 121 and they are mounted along one of their edges in overlapping positions 3~
to the rear frame 16 of the soil compactor 10. They are bolted together by a pair of bolts, one through each outer corner of the plates 120, inserted through a pair of support tubes. The ROPS arm 26 passes -through the corresponding slots in these plates below the point at which the ROPS arm 26 is mounted to an outrigger 122 located on the subframe :L8. The first isolator 116 is enclosed within the space formed by the two parallel plates 120. The ROPS arm 26 is bolted to the outrigger 122 by means of a plate 123 disposed between the outrigger 122 and the ROPS arm 26. A similar plate 123 is bolted to the subframe 18 at the other end of the outrigger 122. Each ROPS arm 26 is also mounted to the rear frame 16 of the vehicle via the isolator 116 as described more fully below.
As best seen in Fig. 7a, the first isolator 116 consists of an inner isolator plate 124 and an outer isolator plate 126. These plates 124, 126 are parallel to and spaced apart from each other and lie in planes perpendicular to the first and second parallel plates 120 and parallel to the plane of the ROPS arm 26. The ROPS arm 26 is bolted to and bisects the outer isolator plate 126.
The inner isolator plate 124 is spaced from the ROPS arm 26 and is joined at its top and bottom edges to the parallel plates 120 which thus additionally serves as a mount for the first isolator 116. A ROPS block 127 is placed at each of the upper and lower edges of the inner isolator plate 124 between the inner isolator plate 124 and rear frame 16 ad~acent each of the two parallel plates 120. Vertical and horizonal bolts secure the rear frame 16 and parallel plate 120 to the ROPS block 127.
The outer isolator plate 126 is bolted to the inner face of the ROPS arm 26. The two isolator plates 124, 126 are generally perpendicular to the two parallel platas 120. A rubber shock absorber 128 flexibly connects 8~3~
the two isolator plates 124, 126 so that they can move relative to one another either vertically or horizontally.
This structure limits the travel of the subframe 18 relative to the rear frame 16 as, for example, when the vehicle is lifted off the ground via the ROPS 24.
In the preferred embodiment of this invention, the ROPS arm 26 is slanted downwardly toward the front of the vehicle, and is not perpendicular to the ground.
Preferably the inner and outer isolator plates 124, 126 are thus also tilted slightly with respect to the ground.
It can be appreciated that a variety of positions for the isolator plates 124, 1~6 are possible depending upon the precise structure of the ROPS arm.
As best seen in ~ig. 7 the second isolator 118 has a structure substantially the same as the first isolator 116. Reference numerals with the suffix "a"
indicate corresponding parts. The second isolator 118, however, is located to the rear of the first isolator 116, inwards of the rear frame 16. The two isolator plates 124a, 126a are again parallel spaced plates flexibly connected by a rubber shock absorber 128a . The outer isolator plate 125a is bolted to the rear frame 16 as shown in FigsO 5 and 6. As best seen in Fig. 7, the other, inner isolator plate 124a lies within the rear frame 16 spaced from the outer isolator plate 126a. The inner isolator plate 124a is joined at one edge to the front wall panel 130 of the tank 132 of the vehicle. The two isolator plates 124a, 126a can move relative to one another either vertically or ho~izontally. A shrouding 134 protects the isolator 118. An identical second isolator 118 is disposed in a corresponding position on the right hand side of the vehicle, and the shrouding is shown removed on the left hand side.
As best seen in Fig. 6, the operator's station ~o~ r3 20 of the soil compactor 10 contains a rubber bumper 136 mounted at the base of the station 20. The engine cover 138 of the vehicle is integral with the operator's station 20 and, can be lifted up by means of a hinge located at the back of the vehicle. The rubber bumper 136 rests on an operators platform foot plate 137 when the engine cover 138 is closed. The rubber bumper 136 absorbs vibrations to protect the operator's station 20 fxom road shock and irregularities transmitted through the rear frame 16.
As best seen in Fig. 5, the drum plate 36 contains a cover plate 140 fastened thereto. The cover plate comprises a generally rectangular metal sheet having a perforations (not shown) at either side of its bottom edge and having a rounded top edge. The perforations enable the coverplate 140 to be secured to the drum plate 36 by means of bolts 142 and corresponding perforations (not shown) in the drum plate 36. The cover plate 140 provides a mechanism to check the hydraulic oil level in the vibratory assembly 96.
As best seen in Figs. 5 and 7, the tank 132 is a dual hydraulic oil and fuel tank of generally rectangular shape. It contains a rear panel 144 which slopes downward toward the vehicle a~ its base. ~he tank 132 also has a top wall panel 146, two side wall panels 148 and a front wall panel 130. A divider plate 150 bisects the tank 132 across its cen~re extending between the front wall panel 130 and rear wall panel 144 from top to bottom of the tank. The divider plate 150 serves to separate the fuel subtank 152 of the tank 132 (located on the right side of the vehicle) from the hydraulic oil subtank 154 of the tank 132 (located on the left side of the vehicle).
Each subtank contains a s~iffener arm 156 which extends between opposing front 130 and rear walls 144 of the tAnk 132 whilst permitting free flow of oil hetween the two parts of each tank. The hydraulic oil subtank 154 contains a baffle 158 which extends from the front wall panel 130 of that subtank 154. The baffle 158 is substantially straight near the front wall pan~l 130 and slants toward the left side wall panel as it extends closer to the rear wal] panel 144. The baffle 158 blocks returning oil from mixing directly wikh e~iting oil. The hydraulic oil subtank 154 also contains an elbow 160 having an internal passage. The elbow 160 is located below the baffle 158 and extends from the front wall panel 130 and curves toward the left side wall panel of the vehicle. The elbow 160 connects with a hydraulic supply hose (not shown) through which hydraulic oil exits the hydraulic oil subtank 154. The elbow 160 contains a hydraulic screen (not shown) disposed in its passage to filter the oil.
The hydraulic oil subtank 154 contains a hydraulic oil filler hole 162 disposed in the top wall panel 146 of the tank 132. It also contains a coupling 164 in the top wall panel 146 where hydraulic oil returns from the vibratory circuit. Another coupling (not shown) is located in the front wall panel 130 through which hydraulic oil returning from the cooling circuit passes.
The fuel subtank 152 contains a fuel filler hole 166 for entering fuel which is disposed in the top wall panel 146 of the tank. The fuel subtank 152 contains a fuel sender 168 disposed in the top wall panel 146 for gauging the fuel levelO
As best shown in Figs. 5, 7 and 8, the preferred embodiment of the soil compactor 10 of the in~ention contains a steering arm 170 rotatably connected at one end to the rear frame 16. The forward end of the arm 170 terminates at the hitch 172 of the soil compactor 10. The 2~ 85~
- 1~
hitch 172 consists of a barrel 174 welded to the rear most end of the front frame 14. The barrel 174 opening faces the rear of the vehicle, with the its centre axis lying in the plane of the front frame 14. A port.ion of the front frame 14 extends above and below the barrel 174 and behind the barrel 174 leaving a gap 1.76 between the base of the barrel 174 and the front fra~e 14, as seen in Fig. 5.
As best seen in Fig. 8, the hitch 172 also comprises a shaft 176 mounted on a steering joint 178 by means of a steering hitch weldment plate 180 affixed to the outer surface of the steering joint 178 and facing the barrel 174. The steering joint 178 is a cylinder disposed in an upright position which has a passageway (not shown) disposed through it. The bottom of the steering ~oint 178 abuts the front edge of the rear frame 16. The top o the steering joint 178 abuts an articulation plate 182, which is secured to the rear frame 16. A rotatable articulation pin 186 is disposed through the vertical pin keeper 184 articulation plate 182, steering joint 178 and front edge of the rear frame 16. The articulation pin 186 is journalled in a bearing (not shown) at each of its end~.
Above the articulation plate 182 and lying flat upon it is a vertical pin keeper 184. The vertical pin keeper 184 is joined to the articulation plate 182 and rear frame 16 by means of a bolt located behind the steering joint 178. The pin keeper 184 is able to keep the articulation pin 186 from rotating. The articulation plate 18Z and rear frame 16 have apertures which correspond with the passageway in the steering joint 178.
The steering arm 170 is attached at its forward end in a bracket 188. The bracket 188 is a thin, generally rectangular member ha~ing two opposing rounded faces at the front end of the bracket 188 with corresponding holes extending through the thickness ~he two faces. There is a gap between the faces, so that an attachment member 190 welded to and extending outwardly from the side of the steering joint 178 fits in the gap.
The attachment member 190 has a circular hole corresponding to the hole in the bracket 188. A pin 192 is mounted upright through the bracket 188 and attachment member 190. Two washers 194 are placed fl.at at either end of the pin 192 on the Ou~Qr faces of the bracket 188. This arrangement permits the steering arm 170 to pivot about the head of the bracket 188.
The articulated steering mechanism just described gives a better surface finish, as compared to skid steer compactors. This latter type of compactor tends to disrupt the surface when steeringl which is not the case here.
The preferred embodiment of this in~ention thus achieves the objective of providing full isolation from both front drum and rear wheel vibration by the combination of a operator's station having a rubber shock absorber at its base, and a rear frame mounted to the subframe by rubber isolation mounts. It can be appreciated that a variety of elastomeric mat~rials and means of connection can be provided for said isolators~
Claims (22)
1. A vehicle for compacting soil or other granular materials comprises:
a) a front frame;
b) at least one compacting drum rotatably mounted on the front frame;
c) a rear frame joined to said front frame;
d) a subframe mounted on said rear frame which contains the operator's station for said rear frame; and e) isolation mounting means mounting said subframe to said rear frame.
a) a front frame;
b) at least one compacting drum rotatably mounted on the front frame;
c) a rear frame joined to said front frame;
d) a subframe mounted on said rear frame which contains the operator's station for said rear frame; and e) isolation mounting means mounting said subframe to said rear frame.
2. A vehicle as claimed in claim 1, wherein two compacting front drums are mounted on said front frame and two rear wheels are mounted on said rear frame, and which includes a hitch joining said rear frame to said front frame, which hitch permits movement of said front frame about a vertical axis and a longitudinal horizontal axis relative to said rear frame, and which vehicle includes a steering mechanism for pivoting said front frame relative to said rear frame about said vertical axis, and a vibratory mechanism mounted on said front frame for imparting vertical vibratory forces to said front drums.
3. A vehicle as claimed in claim 2, wherein the vibratory mechanism is mounted within said front drums.
4. A vehicle as claimed in claim 3, which includes drum hydraulic drive motors mounted within said front drums for driving said front drums and wherein the vibratory mechanism is driven by a vibratory hydraulic motor, with hydraulic supply hoses for said drum and vibratory hydraulic drive motors passing between said two front drums, said front drums being spaced sufficiently to provide a passage for said hydraulic hoses.
5. A vehicle as claimed in claim 2, wherein said isolation mounting means comprises first isolators at the front of the subframe and second isolators at the rear of said subframe, connecting said subframe to said rear frame.
6. A vehicle as claimed in claim 5, wherein the operator's station is separate from the subframe and wherein the isolation mounting means includes a resilient mounting means between the operator's station and the subframe.
7. A vehicle as claimed in claim 5 or 6, which additionally comprises a rollover protection structure having a vertical arm located alongside each side of said subframe and secured to said first isolators, and wherein the front of said subframe is mounted on a transverse outrigger, whose ends are secured to said vertical arms to support said subframe.
8. A vehicle as claimed in claim 5, wherein said first and second isolators comprise resilient isolation mounts mounted in pairs.
9. A vehicle as claimed in claim 8, which includes, for each first isolation mount, a pair of spaced apart plates extending out from the rear frame, with said first isolation mount mounted between those two plates and the plates including slots adjacent the ends thereof, wherein a respective vertical arm extends through those slots and is secured to the respective first isolation mount.
10. A vehicle as claimed in claim 9, which includes a tank supported by said subframe located at the rear of said vehicle.
11. A vehicle as claimed in claim 10, wherein said tank is divided into two separate compartments, one for hydraulic oil and the other for fuel.
12. A vehicle as claimed in claim 5, g and 11, wherein said vibratory mechanism is mounted within the front drums and comprises a pair of shafts bearing eccentric weights and a hydraulic drive motor for driving the shafts, the shafts being driven in opposite directions and arranged to provide a net vertical vibratory force without any significant horizontal force, and which includes hydraulic drive motors for the drums mounted within the drums, all the hydraulic motors having hydraulic supply hoses extending between the two drums to the rear frame with the drums sufficiently spaced to provide a passage for the hydraulic hoses.
13. A vehicle as claimed in claim 4, wherein said front frame comprises a vertical plate extending between the two front drums, and said hydraulic drive motors for said drums are mounted to said front frame and each includes a spindle housing and bearings mounted thereon, on which bearings a respective drum is mounted, and wherein said vibratory mechanism is mounted within the front drums above said spindle housings and comprises a pair of shafts bearing eccentric weights and a hydraulic drive motor for driving the shafts, the shafts being driven in opposite directions and arranged to provide a net vertical vibratory force without any significant horizontal force.
14. A vehicle as claimed in claim 13, wherein said isolation mounting means comprises first isolators on the front of the subframe and second isolators on the rear of the subframe, connecting said subframe to said rear frame, and wherein the vehicle additionally comprises a rollover protection structure having a vertical arm located along each side of said subframe and secured to said first isolators, and wherein the front of said subframe is mounted on a transverse outrigger whose ends are secured to said vertical arms to support said subframe.
15. A vehicle for compacting soil or granular material, the vehicle comprising:
a) a front frame;
b) a pair of compacting drums rotatably mounted on either side of the front frames;
c) a rear frame pivotally attached to the front frame of a pivotal movement around a vertical axis;
d) for each drum, a hydraulic drive motor mounted on the front frame within the respective drum;
e) a vibratory mechanism including a respective hydraulic drive motor mounted on the front frame within the compacting drums, for imparting vibratory action through the front frame to the compacting drums.
a) a front frame;
b) a pair of compacting drums rotatably mounted on either side of the front frames;
c) a rear frame pivotally attached to the front frame of a pivotal movement around a vertical axis;
d) for each drum, a hydraulic drive motor mounted on the front frame within the respective drum;
e) a vibratory mechanism including a respective hydraulic drive motor mounted on the front frame within the compacting drums, for imparting vibratory action through the front frame to the compacting drums.
16. A vehicle as claimed in claim 15, which includes a subframe having an operator's station, and isolation mounting means mounting the subframe to the rear frame.
17. A vehicle as claimed in claim 16, wherein the isolation mounting means comprises first isolators at the front of said subframe and second isolators at the rear of said subframe, and wherein the vehicle includes a rollover protection structure having a vertical arm located along side of each side of said subframe and secured to the first isolators, and wherein the front of said subframe is mounted on a transverse outrigger, whose ends are secured to said vertical arms to support said subframe.
18. A drive for driving the compacting drum of a compactor vehicle which comprises:
a) a hub for fastening to said drum and for rotation with said drum;
b) a motor having a main housing and a rotatable shaft;
c) A spindle housing fastened to said main housing surrounding said shaft which is interposable between said hub and said shaft, and d) a plurality of bearings disposed between said hub and said spindle housing.
a) a hub for fastening to said drum and for rotation with said drum;
b) a motor having a main housing and a rotatable shaft;
c) A spindle housing fastened to said main housing surrounding said shaft which is interposable between said hub and said shaft, and d) a plurality of bearings disposed between said hub and said spindle housing.
19. A drum drive as claimed in claim 18 wherein said bearings are cylindrical roller bearings.
20. A drum drive as claimed in claim 19 wherein said spindle housing comprises a cylindrical sleeve having a flange at one end, which flange is fastened to said motor housing, and wherein said hub is fastened to a drive plate rotatable with said shaft and located at the other end of said sleeve, adjacent said sleeve.
21. A drum drive as claimed in claim 20 wherein said cylindrical roller bearings are separated by at least one bearing spacer encircling said sleeve, said spacer being adapted to locate and separate said cylindrical roller bearings.
22. A drum drive as claimed in claim 21 wherein said cylindrical roller bearings are separated by a pair of bearing spacers which define a notch and which includes a thrust plate engaging said notch and secured within said hub.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA 2042890 CA2042890A1 (en) | 1991-05-17 | 1991-05-17 | Soil compactor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CA 2042890 CA2042890A1 (en) | 1991-05-17 | 1991-05-17 | Soil compactor |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2042890A1 true CA2042890A1 (en) | 1992-11-18 |
Family
ID=4147621
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA 2042890 Abandoned CA2042890A1 (en) | 1991-05-17 | 1991-05-17 | Soil compactor |
Country Status (1)
| Country | Link |
|---|---|
| CA (1) | CA2042890A1 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3034347B1 (en) | 2014-12-18 | 2017-05-10 | Hamm AG | Soil processing machine, in particular soil compactor |
-
1991
- 1991-05-17 CA CA 2042890 patent/CA2042890A1/en not_active Abandoned
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP3034347B1 (en) | 2014-12-18 | 2017-05-10 | Hamm AG | Soil processing machine, in particular soil compactor |
| US10214087B2 (en) | 2014-12-18 | 2019-02-26 | Hamm Ag | Ground processing machine, in particular compactor |
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| Date | Code | Title | Description |
|---|---|---|---|
| FZDE | Dead |