CA1220373A - Vibratory mechanism - Google Patents
Vibratory mechanismInfo
- Publication number
- CA1220373A CA1220373A CA000458390A CA458390A CA1220373A CA 1220373 A CA1220373 A CA 1220373A CA 000458390 A CA000458390 A CA 000458390A CA 458390 A CA458390 A CA 458390A CA 1220373 A CA1220373 A CA 1220373A
- Authority
- CA
- Canada
- Prior art keywords
- shaft
- mass
- fluent
- chamber
- walls
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
- B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
- B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
- B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
- B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
- B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
- B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
- B06B1/10—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy
- B06B1/16—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of mechanical energy operating with systems involving rotary unbalanced masses
- B06B1/161—Adjustable systems, i.e. where amplitude or direction of frequency of vibration can be varied
- B06B1/162—Making use of masses with adjustable amount of eccentricity
- B06B1/165—Making use of masses with adjustable amount of eccentricity with fluid masses or the like
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
- B65G—TRANSPORT OR STORAGE DEVICES, e.g. CONVEYORS FOR LOADING OR TIPPING, SHOP CONVEYOR SYSTEMS OR PNEUMATIC TUBE CONVEYORS
- B65G27/00—Jigging conveyors
- B65G27/10—Applications of devices for generating or transmitting jigging movements
- B65G27/16—Applications of devices for generating or transmitting jigging movements of vibrators, i.e. devices for producing movements of high frequency and small amplitude
- B65G27/18—Mechanical devices
- B65G27/20—Mechanical devices rotating unbalanced masses
Abstract
VIBRATORY MECHANISM
ABSTRACT OF DISCLOSURE
A road compacting drum is equipped with a dual amplitude, rotational, vibratory mechanism. A shaft rotatably mounted on the drum supports eccentric weights.
Casings secured to the shaft adjacent the weights have chambers accommodating fluent mass. The fluent mass comprise metal members, as steel balls, shot or liquid metal, that move to a first location in the chamber upon rotation of the shaft in one direction to increase the amplitude of the vibration of the shaft and drum.
the fluent mass flows to a second location in the chamber in response to rotation of the shaft in a direction opposite the one direction to generally balance the shaft to reduce the amplitude of vibration of the shaft and drum.
ABSTRACT OF DISCLOSURE
A road compacting drum is equipped with a dual amplitude, rotational, vibratory mechanism. A shaft rotatably mounted on the drum supports eccentric weights.
Casings secured to the shaft adjacent the weights have chambers accommodating fluent mass. The fluent mass comprise metal members, as steel balls, shot or liquid metal, that move to a first location in the chamber upon rotation of the shaft in one direction to increase the amplitude of the vibration of the shaft and drum.
the fluent mass flows to a second location in the chamber in response to rotation of the shaft in a direction opposite the one direction to generally balance the shaft to reduce the amplitude of vibration of the shaft and drum.
Description
VIBRATORY Illusions YIELD OF INVENTION
The invention is in the field of vibration mechanics utilizing rotational mechclnisms for changing the amplitude of the vibration of an apparatus. The vibratory mechanism is usable in road compactillg machines having drums that are vibrated to achieve a desired compacting function.
BACKGROUND OF INVENTION
In one known self propelled vibrating road roller the compactor drum is vibrated at 1700 rum by a dual amplitude vibratory mechanism which utilizes a swinging eta. The compactor drum rotates at vehicle speed as the vehicle moves forl~arcL. The drum is supported on the vehicle frame by anti-vibration mountillgs. An axial, reversible drive shaft at the center of the drum is driven by a hydraulic motor from the vehicle. The drum shaft has, in addition to a fixed eccentric weight, a hinge pin parallel to the axis of the shaft, a pocket for accommodating the swinging weight and stops to limit the travel of the swinging weight When the shaft rotates in one direction the swinging weight turns on the hinge pin to an eccentric position which adds to the fixed eccentric weight and increase the eccentric moment.
inn the shaft rotation is reversed by the operator, the Z5 hinged weight turns again on the hinge pin to the extent limited by the remaining stop and subtracts from the eccentric moment. The impact of the weight on the stops at each halt, start and reversal eventually produces metal particles in the mechanism which contaminate the bearings causing consequential failure and the drum must be disassembled to give access for repair.
SEYMOUR OF INVENTION
"
~`;"`"~
37~
The invention is in the field of vibration mechanics utilizing rotational mechclnisms for changing the amplitude of the vibration of an apparatus. The vibratory mechanism is usable in road compactillg machines having drums that are vibrated to achieve a desired compacting function.
BACKGROUND OF INVENTION
In one known self propelled vibrating road roller the compactor drum is vibrated at 1700 rum by a dual amplitude vibratory mechanism which utilizes a swinging eta. The compactor drum rotates at vehicle speed as the vehicle moves forl~arcL. The drum is supported on the vehicle frame by anti-vibration mountillgs. An axial, reversible drive shaft at the center of the drum is driven by a hydraulic motor from the vehicle. The drum shaft has, in addition to a fixed eccentric weight, a hinge pin parallel to the axis of the shaft, a pocket for accommodating the swinging weight and stops to limit the travel of the swinging weight When the shaft rotates in one direction the swinging weight turns on the hinge pin to an eccentric position which adds to the fixed eccentric weight and increase the eccentric moment.
inn the shaft rotation is reversed by the operator, the Z5 hinged weight turns again on the hinge pin to the extent limited by the remaining stop and subtracts from the eccentric moment. The impact of the weight on the stops at each halt, start and reversal eventually produces metal particles in the mechanism which contaminate the bearings causing consequential failure and the drum must be disassembled to give access for repair.
SEYMOUR OF INVENTION
"
~`;"`"~
37~
-2-The invention concerlls a dual amplitude, rotational, vibratory mechanism in which the alllplitucle of the vibration can be changed by reversing the direction of the rotation of the mechanism. The vibratory mechanism is usable with a compactor drum of a road compacting machine. Tile utility of the vibratory mechanism is not limited to road compacting machines.
The vibratory mechanism can be usecl-~it}l mineral crushers and sep~lratols, feed mechanisms for particulate material lo and like machines.
The vibratory mechanism has a shaft rotatable molted on the member to be vibrated. weight means are eccentrically associated with the shaft to provide a first eccentric mass which causes the shaft to vibrate upon rotation thereof. leans mounted on tile shaft has a fluent second Isles Lucia upon rotation thereof. leans mounted on the shift has a fluent second mass which loll shut rotation in one direction flus to a first position to augmellt -the eccentric distribution o-E the first mass thereby producing a high amplitude vibration of the shaft and member and upon rotation of the shaft in tile opposite direction the fluent second mass flows to a second posit which lends to balclnce the eccentricity end produce low amplitude vibration of the shalt and member.
In one embodiment of the inveJltioll, a shaft is rota-tally mounted on a housing with a plurality of bearings.
The housing is secured to a drum of a road compacting machine. weight means Eddy to the shaft provides an eccentric first mass. leans having a fluent second mass includes a casing or capsule secured to the shaft. The casing has a chamber accommodatillg the fluent second mass.
Tile fluent second mass may be a plurality of metal members such as small steel balls, cast iron shot, or liquid metal. The casing has at least one partition located withiJl the chamber which upon rotation of the shaft con-fines tile fluent second mass to separate portions of the chclmber to either augment or balance the first mass. The shaft is rotated with a reversible motor. When the shaft . . .
The vibratory mechanism can be usecl-~it}l mineral crushers and sep~lratols, feed mechanisms for particulate material lo and like machines.
The vibratory mechanism has a shaft rotatable molted on the member to be vibrated. weight means are eccentrically associated with the shaft to provide a first eccentric mass which causes the shaft to vibrate upon rotation thereof. leans mounted on tile shaft has a fluent second Isles Lucia upon rotation thereof. leans mounted on the shift has a fluent second mass which loll shut rotation in one direction flus to a first position to augmellt -the eccentric distribution o-E the first mass thereby producing a high amplitude vibration of the shaft and member and upon rotation of the shaft in tile opposite direction the fluent second mass flows to a second posit which lends to balclnce the eccentricity end produce low amplitude vibration of the shalt and member.
In one embodiment of the inveJltioll, a shaft is rota-tally mounted on a housing with a plurality of bearings.
The housing is secured to a drum of a road compacting machine. weight means Eddy to the shaft provides an eccentric first mass. leans having a fluent second mass includes a casing or capsule secured to the shaft. The casing has a chamber accommodatillg the fluent second mass.
Tile fluent second mass may be a plurality of metal members such as small steel balls, cast iron shot, or liquid metal. The casing has at least one partition located withiJl the chamber which upon rotation of the shaft con-fines tile fluent second mass to separate portions of the chclmber to either augment or balance the first mass. The shaft is rotated with a reversible motor. When the shaft . . .
3'~3 is notated in a first directioll the firelight mass flows to the first position theIeb ploducillg a hill amplitude vibration of the shaft end member Lyle the shaft is notated in the reverse or second direction the -fluent mass moves to the second direction the fluent mass moves to the second location thereby plodlcillg a 1 amplitude vibra-tioll of the shift all member.
knothole emboclilllent of tile inventioll has a shaft drivable connected to a reversible motor. The shift is mounted Ire rotation on . mclllhel such as 1 drum pair of cozily s h.lvillg shelters for accollllllodltillT fluellt miss are mounted on axially space portions of the shaft.
Lowry exalllp1c?, the casings Clue be mo~llltecl acljlcellt opposite ends of the shaft. Eschew casillg has partition melts that separate the chlrllber into first all second locations for the fLuellt miss. Iota Melissa are molted Oil the shclft adjacent etch casino. The weight mecllls is positioned adjacent the first locations. Ire motor operates to rotate tile shift in a first directioll causing the fluent mass to flow to the first pOSitiOIl thereby producillg a high amplitude vibratioll Or the shift and mulberry. Lyle the motor drive is revc?}sel tile shclft if notated in a second direction or opposite tile First direction CclUSillg the fluellt mass to flow to the seconcll)osition thereby proclucillg a low amplitude vibration of the shaft and mom-berm The pair of casings accolllmodatillg fluent second mass dispose symmetrically about the aye center of the shaft are preferred over a single central casing all weight meals. the use of a single casing wreckers a stiffer shift to resist deflection.
n alterllate emboclilllellt ox the vibratory mechln1sm, lay at shift rotatable mounted in an eccentric position relative to the support bearings. on additiolla1 eccentric mass Clue be fixed to the shift. Maxilllulll difference in the eccentric moment between high arid low amplitude modes is achieved ~it]l a concentric path for the fluent second mass. ~cceptclb1e performance is achieved with an eccentric 3~73 Lo path or ring-like path containing pockets o-r lobes for accommodating the flue1lt second mass.
DISCRETE OF DRYING
Figure 1 is an end view of a drum of a vibrating 5 roller of a roach compacting machine equipped White the vibratory mechclnism of the invention;
Figure 2 is a foreshortened sectional vie take along the line 2-2 of figure l;
Figure 3 is an enlarged sectional vie of a vibratory mechanism muted Owe a slot as S}10~11 in logger I;
Figure is a sectional vie taken along the line I
of figure 3 show lug the location Or the fluel1t second muss in the high an1r)litucle mode;
Figure 5 is a sectional vie taken along the line 5-5 of Figure 3 showing the c1istribution of the fluent saclike mass during stroboscopic excommunication;
Figure 6 is a sectional view taken along the line 6-6 Ott figure 3;
l inure 7 is a sectional vowel similclr to Figure 3 showing the location of the fluent seconc1 mass in low an1plitude mode; and figure 8 is a sectio11cll vie taken along the line 8-8 of Figure 7.
DESCRIPTION Of: PROWLER D E~IBODI~IENT
A sol E propelled vibrati11g roller in hill -this emboc1i11lent of -the invention is usual has a front drum and a rear Crimea each mounted in its own frame on anti-vibration mounti11gs. Each drum has a cylindrical steel shell having dimensions of 1500mm diameter 2000mm long and about 25m111 -thick. The drum weig11s about 3500 kg. The my value of the eccentric mechanisms suitable for rollers of the heavier class is in the range from 4-l0 kg metros.
The dry c1isplace111c?l1t is of the order o 3 mm at high amplitude mode and about lo mm at low amplitude mode.
Referring to Figures l and 2 the drum has a Solon-Dracula shell 1 and a pair of circular plates or ends 2 and 3 located inwardly from the opposite ends of shell l.
End 2 has a central aperture 4 aligned with a central 3~3 aperture? I in end 3. A shaft 5 and vibratory mechanisms 23 and 24 pass through one of the apertures and are located between ends 2 and 3. Shaft 5 is a steel shclft having sufficient size to resist deflection. Preferrclbly shaft 5 has a diameter of 188mm. Other shaft sizes can be used.
A cup-shapecl cylindrical housing 6 extends through aperture 4. lousing 6 has an outwardly directed flange 7 secure to end 2 with bolts 21. A bearillg 8 located within housing 6 rotatable supports one end of shaft 5 on housing 6 housing 6 has an ou-twlldly directed stub axle 9. bearing 11 supports a sleeve 12 on axle 9.
Sleeve 12 is secured to a plate 13 used to support the drum 1 Oil the vehicle (not shown).
End 3 his a central aperture LO acco~mnodatillg a cup-shape housing lo. lousing 15 has an outwcLrdly directed flange 16 secured to end 3 with bolts 17. A bearing 18 locate within hOUSillg 15 rotatlbly supports one end of shaft 5 Oil housillg 15. Bcarillgs 8 end 18 mount shaft 5 on housings 7 and Lo for rotatioll about -the longitudillcll ax-is of shift 5. Alterllatively, slot 5 can be eccentric calmly mountc?l in bearings 8 all 18. I-lous-ings 7 arid 15 close? apertures 4 allot 11 and prevellt the entrclnce of water and foreigll matter into tile? Clara chLIllber between ends 2 and 3.
lousing 15 has an outwardly directed stub axle 19 accommodating a bearing 20. A sleeve AL mounted Oil bearing 20 is secured to a plate 22. Plates 13 and 22 are attached to vehicle structure to secure druTIl 1 to tile vehicle.
A reversible hydraulic motor 23 is connected to end I of shaft 5. lottery 23 is connected with suitable ho-clraulic lines to a source of hydraulic fluid under pressure and control valves (not shown) which allele the operator of the vehicle to control the operation of motor 23 to chLIlge the direction of rotation of shaft 5 as well as the speed Or rotation of snail 5.
A pair of weights 25 and 26 are mounted on shaft 5 adjacent the opposite ends thereof. weights 25 and 26 have eccentrically located masses which cause shaft 5 3'73 I, to vitiate whelp Kit is rotate. so Shelley yin Figure 6, mass 25 has all arcucl-te configulclt:ion off set from the axis of rotation of shift 5 end an arcuate length less than 180 degrees. Weight 26 has a shape and displace-mint that is the same Claus Weight 25.
Retulrl:irlg to figure 2, a pair of vibratory units indicated generally at 27 and 28 are mounted on shaft 5 adjacent weights 25 and 26. Vibratory units 27 allele 28 are identical yin structure. Ike following description is cl:irectccl to vibratory Ulli t 27. As shown in inure 3, vibrcltory unwept 27 hclS at sealed, hollow capsule or casing that awoke lodatc~s a fluent mass 33, 'r}lC CclSillg has circular ells alleles 2') end 30 molted Oil shaft 5. Aye circumferential outer wall or raceway 31 is secured to the Outs` per.ipllcll edges of end wakeless 29 all 30 and define throttle a chamfer 32. Chamber 32 its concelltric with the acts of rotation of shaft 5. Fluent mass 33 is located in chamber 32. The fluell-t mass 33 is a movable weight, Suckle as plurality of metal members, steel balls, metal shot, likelihood Innately, sand, end like flyable ballast material As shown yin figures 4, 5, Allis 8 less thcln half owe chclmber 32 is fillet with fluent Lucy 33 or walls 34 and 35 are locate in chamber 32. Walls 34 and 35 are secured to opposite stales of shut 5 all extend along separate choral lines to outer wall 31. Wakeless 34 ail 35 are stops for Fluent mass 33 that David chamber 32 into a first portion AYE and a second portion 32B. Chamber portions AYE and 32B are located diametrically opposite Eros each other as shown in Figure 4. Wall 29 has a normally closed port or opening 36 through which fluent mass 33 is introduced islet chamber 32. Walls 34 and 35 can be substant:icl:lly radical walls that extend from shaft 5 to outer allele 31. These walls can be angularly disposed from each other at an angle from about 80 to 135 degrees and define the oppositely disposed chambers AYE and 32B
for fluent mass 33.
In use, the maxilllulll vibration amplitude is achieved by rotating shaft 5 in the direction of the arrow 38, as 37~3 shown yin loggers end 5. IIycIIaulic motor 23 Irises shaft 5 :incIepeIldent of the steed o-f rotation of the shell 1. Fluent mass 33 moves Pinto the chamber port lion 32~ agaiIlst Wylie 35. so shown in inure 3 fluent mass 33 is located acljaceIlt the eccentric first mass or weight 25 thereby increasing the eccentric mass that rotates with shaft 5. This increases the amputee of the vibration of shaft 5 ail shell 1.
The rotat:ioTI of shaft 5 in the opposite direction indicated by tie aureole 9 yin FilJule causes foe t mass 33 to move into second chaIllber portion 32I3. lo shown in inure 7 chlmbeI pollution 32B is diaIlletrical1y opposite weight 25 ebb the tlueIlt second mass couIlteracts weight 25 arid tents to bcll.allce shaft 5. This refuges the amply-tulle of the varietal of shaft 5 and Shelley 1.
Re:Eerr:iIlg now to Figure 5 a pheIlomenoll is observahlecIurirlg stroboscopic examination of the shaft 5 end unit 27 when revolving at working speed yin the direction of arrow 35. UncIer the combiIled effects of Friction end Sinatra-phyla force the foliate mass 33 assumes tile crescent shapeclSUrf,lCe as Shea at 37. The magnitude of the eccentric moment of the? flueIlt mclss 33 yin practice varies only slightly from the mc~n:itucIe of tile eccentric moment owe the tlIealeticcll :flueIlt miss and is considered to be with-yin acceptable Torrance limits. The actual eccentric moment is Seattle less than the theoretical value but can easily be brought up to the theoretical value by a small increase yin mass of the fluent mass.
Tile Relative ~IagnitIlIe of Eccentric immunity of the foliate mass can be ca.IculIted as phallus:
Let hi = total eccentric moment required for high aIllp:litucIe mode.
Let aye = total. eccentric momeIlt required for low amplitude mode.
where a = ratio of low amplitude high Let x = eccentric moment of the fixed eccentric mass Let y = eccentric moment of the fluent mass . . .
3'~3 The following simult.lrleous e~luatiolls apply A - y = Allah . . . . . . . , , , , , .. . . . . . ?
by s~lbtrclction S my = cull . . y = Ill . . . . . . . . . . . . . . . . . . . 3 substitutillg in eclucltion Centrally a - owe Titus low amplitude is hull f the high alllplitucle but by alter:illg the ratio ox fluellt Isles 33 to the lived mass 25 a can be made to by? Other` than 0. 5.
Ike advlntagcs of the vibratory mecllanislll are as follows: Impact loads are rellclered insigTli~iclnt be--cause the fluent Isles 33 constitute multiple Smalley masses which accclelate end decelerate Without producing the impact clalllclge associated with a swinging weight.
Ike E:Lueilt mass 33 is conEinecl~iitllill a scaled chasing Welch eliminates bcarillg deluge Eros consequential failure. Ire Cls-illgs of Ullits Z7 and 28 are maintenance free and are located in the protected drywall challlber.
While there his bell shown end described the Libra-tory mechln-islll of the invention it is understood that chclnges in the structure all use owe the mechanism allay be mclde by those skilled in the art without departing from -tile invention. For example weights 25 and 26 can be crescent-shapecl pieces of metal that are secured by welds or the like to the end Willis 29 of vibratory units 27 all 28. The internal walls 34 all 35 can have other Slops 9 Suckle as radial to provide the separate chamber portions 32~ and 32B for the fluent second mass 33. The outer wall 31 can have a plurality of symmetrical lobes for accommodating the fluent second mass 33.
the invention is defined in the following claims.
knothole emboclilllent of tile inventioll has a shaft drivable connected to a reversible motor. The shift is mounted Ire rotation on . mclllhel such as 1 drum pair of cozily s h.lvillg shelters for accollllllodltillT fluellt miss are mounted on axially space portions of the shaft.
Lowry exalllp1c?, the casings Clue be mo~llltecl acljlcellt opposite ends of the shaft. Eschew casillg has partition melts that separate the chlrllber into first all second locations for the fLuellt miss. Iota Melissa are molted Oil the shclft adjacent etch casino. The weight mecllls is positioned adjacent the first locations. Ire motor operates to rotate tile shift in a first directioll causing the fluent mass to flow to the first pOSitiOIl thereby producillg a high amplitude vibratioll Or the shift and mulberry. Lyle the motor drive is revc?}sel tile shclft if notated in a second direction or opposite tile First direction CclUSillg the fluellt mass to flow to the seconcll)osition thereby proclucillg a low amplitude vibration of the shaft and mom-berm The pair of casings accolllmodatillg fluent second mass dispose symmetrically about the aye center of the shaft are preferred over a single central casing all weight meals. the use of a single casing wreckers a stiffer shift to resist deflection.
n alterllate emboclilllellt ox the vibratory mechln1sm, lay at shift rotatable mounted in an eccentric position relative to the support bearings. on additiolla1 eccentric mass Clue be fixed to the shift. Maxilllulll difference in the eccentric moment between high arid low amplitude modes is achieved ~it]l a concentric path for the fluent second mass. ~cceptclb1e performance is achieved with an eccentric 3~73 Lo path or ring-like path containing pockets o-r lobes for accommodating the flue1lt second mass.
DISCRETE OF DRYING
Figure 1 is an end view of a drum of a vibrating 5 roller of a roach compacting machine equipped White the vibratory mechclnism of the invention;
Figure 2 is a foreshortened sectional vie take along the line 2-2 of figure l;
Figure 3 is an enlarged sectional vie of a vibratory mechanism muted Owe a slot as S}10~11 in logger I;
Figure is a sectional vie taken along the line I
of figure 3 show lug the location Or the fluel1t second muss in the high an1r)litucle mode;
Figure 5 is a sectional vie taken along the line 5-5 of Figure 3 showing the c1istribution of the fluent saclike mass during stroboscopic excommunication;
Figure 6 is a sectional view taken along the line 6-6 Ott figure 3;
l inure 7 is a sectional vowel similclr to Figure 3 showing the location of the fluent seconc1 mass in low an1plitude mode; and figure 8 is a sectio11cll vie taken along the line 8-8 of Figure 7.
DESCRIPTION Of: PROWLER D E~IBODI~IENT
A sol E propelled vibrati11g roller in hill -this emboc1i11lent of -the invention is usual has a front drum and a rear Crimea each mounted in its own frame on anti-vibration mounti11gs. Each drum has a cylindrical steel shell having dimensions of 1500mm diameter 2000mm long and about 25m111 -thick. The drum weig11s about 3500 kg. The my value of the eccentric mechanisms suitable for rollers of the heavier class is in the range from 4-l0 kg metros.
The dry c1isplace111c?l1t is of the order o 3 mm at high amplitude mode and about lo mm at low amplitude mode.
Referring to Figures l and 2 the drum has a Solon-Dracula shell 1 and a pair of circular plates or ends 2 and 3 located inwardly from the opposite ends of shell l.
End 2 has a central aperture 4 aligned with a central 3~3 aperture? I in end 3. A shaft 5 and vibratory mechanisms 23 and 24 pass through one of the apertures and are located between ends 2 and 3. Shaft 5 is a steel shclft having sufficient size to resist deflection. Preferrclbly shaft 5 has a diameter of 188mm. Other shaft sizes can be used.
A cup-shapecl cylindrical housing 6 extends through aperture 4. lousing 6 has an outwardly directed flange 7 secure to end 2 with bolts 21. A bearillg 8 located within housing 6 rotatable supports one end of shaft 5 on housing 6 housing 6 has an ou-twlldly directed stub axle 9. bearing 11 supports a sleeve 12 on axle 9.
Sleeve 12 is secured to a plate 13 used to support the drum 1 Oil the vehicle (not shown).
End 3 his a central aperture LO acco~mnodatillg a cup-shape housing lo. lousing 15 has an outwcLrdly directed flange 16 secured to end 3 with bolts 17. A bearing 18 locate within hOUSillg 15 rotatlbly supports one end of shaft 5 Oil housillg 15. Bcarillgs 8 end 18 mount shaft 5 on housings 7 and Lo for rotatioll about -the longitudillcll ax-is of shift 5. Alterllatively, slot 5 can be eccentric calmly mountc?l in bearings 8 all 18. I-lous-ings 7 arid 15 close? apertures 4 allot 11 and prevellt the entrclnce of water and foreigll matter into tile? Clara chLIllber between ends 2 and 3.
lousing 15 has an outwardly directed stub axle 19 accommodating a bearing 20. A sleeve AL mounted Oil bearing 20 is secured to a plate 22. Plates 13 and 22 are attached to vehicle structure to secure druTIl 1 to tile vehicle.
A reversible hydraulic motor 23 is connected to end I of shaft 5. lottery 23 is connected with suitable ho-clraulic lines to a source of hydraulic fluid under pressure and control valves (not shown) which allele the operator of the vehicle to control the operation of motor 23 to chLIlge the direction of rotation of shaft 5 as well as the speed Or rotation of snail 5.
A pair of weights 25 and 26 are mounted on shaft 5 adjacent the opposite ends thereof. weights 25 and 26 have eccentrically located masses which cause shaft 5 3'73 I, to vitiate whelp Kit is rotate. so Shelley yin Figure 6, mass 25 has all arcucl-te configulclt:ion off set from the axis of rotation of shift 5 end an arcuate length less than 180 degrees. Weight 26 has a shape and displace-mint that is the same Claus Weight 25.
Retulrl:irlg to figure 2, a pair of vibratory units indicated generally at 27 and 28 are mounted on shaft 5 adjacent weights 25 and 26. Vibratory units 27 allele 28 are identical yin structure. Ike following description is cl:irectccl to vibratory Ulli t 27. As shown in inure 3, vibrcltory unwept 27 hclS at sealed, hollow capsule or casing that awoke lodatc~s a fluent mass 33, 'r}lC CclSillg has circular ells alleles 2') end 30 molted Oil shaft 5. Aye circumferential outer wall or raceway 31 is secured to the Outs` per.ipllcll edges of end wakeless 29 all 30 and define throttle a chamfer 32. Chamber 32 its concelltric with the acts of rotation of shaft 5. Fluent mass 33 is located in chamber 32. The fluell-t mass 33 is a movable weight, Suckle as plurality of metal members, steel balls, metal shot, likelihood Innately, sand, end like flyable ballast material As shown yin figures 4, 5, Allis 8 less thcln half owe chclmber 32 is fillet with fluent Lucy 33 or walls 34 and 35 are locate in chamber 32. Walls 34 and 35 are secured to opposite stales of shut 5 all extend along separate choral lines to outer wall 31. Wakeless 34 ail 35 are stops for Fluent mass 33 that David chamber 32 into a first portion AYE and a second portion 32B. Chamber portions AYE and 32B are located diametrically opposite Eros each other as shown in Figure 4. Wall 29 has a normally closed port or opening 36 through which fluent mass 33 is introduced islet chamber 32. Walls 34 and 35 can be substant:icl:lly radical walls that extend from shaft 5 to outer allele 31. These walls can be angularly disposed from each other at an angle from about 80 to 135 degrees and define the oppositely disposed chambers AYE and 32B
for fluent mass 33.
In use, the maxilllulll vibration amplitude is achieved by rotating shaft 5 in the direction of the arrow 38, as 37~3 shown yin loggers end 5. IIycIIaulic motor 23 Irises shaft 5 :incIepeIldent of the steed o-f rotation of the shell 1. Fluent mass 33 moves Pinto the chamber port lion 32~ agaiIlst Wylie 35. so shown in inure 3 fluent mass 33 is located acljaceIlt the eccentric first mass or weight 25 thereby increasing the eccentric mass that rotates with shaft 5. This increases the amputee of the vibration of shaft 5 ail shell 1.
The rotat:ioTI of shaft 5 in the opposite direction indicated by tie aureole 9 yin FilJule causes foe t mass 33 to move into second chaIllber portion 32I3. lo shown in inure 7 chlmbeI pollution 32B is diaIlletrical1y opposite weight 25 ebb the tlueIlt second mass couIlteracts weight 25 arid tents to bcll.allce shaft 5. This refuges the amply-tulle of the varietal of shaft 5 and Shelley 1.
Re:Eerr:iIlg now to Figure 5 a pheIlomenoll is observahlecIurirlg stroboscopic examination of the shaft 5 end unit 27 when revolving at working speed yin the direction of arrow 35. UncIer the combiIled effects of Friction end Sinatra-phyla force the foliate mass 33 assumes tile crescent shapeclSUrf,lCe as Shea at 37. The magnitude of the eccentric moment of the? flueIlt mclss 33 yin practice varies only slightly from the mc~n:itucIe of tile eccentric moment owe the tlIealeticcll :flueIlt miss and is considered to be with-yin acceptable Torrance limits. The actual eccentric moment is Seattle less than the theoretical value but can easily be brought up to the theoretical value by a small increase yin mass of the fluent mass.
Tile Relative ~IagnitIlIe of Eccentric immunity of the foliate mass can be ca.IculIted as phallus:
Let hi = total eccentric moment required for high aIllp:litucIe mode.
Let aye = total. eccentric momeIlt required for low amplitude mode.
where a = ratio of low amplitude high Let x = eccentric moment of the fixed eccentric mass Let y = eccentric moment of the fluent mass . . .
3'~3 The following simult.lrleous e~luatiolls apply A - y = Allah . . . . . . . , , , , , .. . . . . . ?
by s~lbtrclction S my = cull . . y = Ill . . . . . . . . . . . . . . . . . . . 3 substitutillg in eclucltion Centrally a - owe Titus low amplitude is hull f the high alllplitucle but by alter:illg the ratio ox fluellt Isles 33 to the lived mass 25 a can be made to by? Other` than 0. 5.
Ike advlntagcs of the vibratory mecllanislll are as follows: Impact loads are rellclered insigTli~iclnt be--cause the fluent Isles 33 constitute multiple Smalley masses which accclelate end decelerate Without producing the impact clalllclge associated with a swinging weight.
Ike E:Lueilt mass 33 is conEinecl~iitllill a scaled chasing Welch eliminates bcarillg deluge Eros consequential failure. Ire Cls-illgs of Ullits Z7 and 28 are maintenance free and are located in the protected drywall challlber.
While there his bell shown end described the Libra-tory mechln-islll of the invention it is understood that chclnges in the structure all use owe the mechanism allay be mclde by those skilled in the art without departing from -tile invention. For example weights 25 and 26 can be crescent-shapecl pieces of metal that are secured by welds or the like to the end Willis 29 of vibratory units 27 all 28. The internal walls 34 all 35 can have other Slops 9 Suckle as radial to provide the separate chamber portions 32~ and 32B for the fluent second mass 33. The outer wall 31 can have a plurality of symmetrical lobes for accommodating the fluent second mass 33.
the invention is defined in the following claims.
Claims (25)
1. vibratory mechanism for vibrating a member comprising: a shaft means for rotatably mounting the shaft on the member weight means eccentrically mounted with respect to said shaft for rotation therewith to vibrate said shift when rotationally driven, means mounted on the shaft having a fluent mass which upon shaft rotation in one direction moves to a first location to augment the eccentric distribution of said weight means thereby producing high amplitude vibration of the member and upon rotation of the shaft in the opposite direction said fluent mass moves to a second location which tends to balance the eccentricity of the weight means to produce low amplitude vibration of the member, and means to selectively rotate the shaft in opposite directions.
2. The mechanism of Claim 1 wherein: the means for rotatably mounting the shaft on the member include bearings rotatably supporting the shaft for rotation about the longitudinal axis thereof.
3. The mechanism of Claim 1 wherein: the weight means is fixed to the shaft adjacent the means mounted on the shaft having a fluent mass and adjacent the first location for the fluent mass.
4. The mechanism of Claim 1 wherein: the fluent mass comprises a plurality of metal members.
5. The mechanism of Claim 1 wherein: the fluent mass comprises a liquid metal.
6. The mechanism of Claim 1 wherein: the means mounted on the shaft having a fluent mass comprise casing means having a chamber accommodating the fluent mass, said chamber having said first and second locations for the fluent mass, said weight means being mounted on the shaft adjacent the first location of the casing means.
7. The mechanism of Claim 1 wherein: the casing means comprises a plurality of casings mounted on the shaft, each casing having a chamber accommodating fluent mass, each chamber having said first and second locations for the fluent mass, each chamber having said first and second locations for the fluent mass, said weight means comprising a plurality of weights mounted on the shaft, at least one weight being located adjacent the first location of each casing.
8. The mechanism of Claim 7 including: partition means located within the chamber of each casing to divide the chamber into the first and second locations.
9. The mechanism of Claim 7 wherein: the fluent mass comprises a plurality of metal members located with-in the chamber.
10. The mechanism of Claim 1 wherein: the means mounted on the shaft having a fluent mass comprises casing means having a chamber for accommodating the fluent mass, said chamber being concentric with the longitudinal axis of the shaft, and at least one par-tition means located within the chamber which upon ro-tation of the shaft confines the fluent mass to a first chamber portion in which the fluent mass augments the eccentricity of the weight means and a second chamber portion in which the fluent mass tends to balance the eccentricity of the weight means.
11. The mechanism of Claim 10 wherein: said partition means comprises a pair of walls, one of said walls having a first section which extends across the chamber defining part of a chord and a second wall having a section that extends parallel to the chord of the first section.
12. The mechanism of Claim 1 wherein: the means mounted on the shaft having a fluent mass comprises a casing means mounted on the shaft, said casing means having a chamber accommodating the fluent mass, and partition means located in said chamber providing said first and second locations for the fluent mass, said partition means comprising a pair of walls located in said chamber, one of said walls having a first section which extends from the axle across the chamber defining part of a chord and a second section extended radially from said shaft located generally perpendicular to the first section, the other wall having a first section which extends from the shaft generally parallel to the chord of the first wall and a second section which is radial with respect to the shaft, said walls lying in the same semi-circle of the chamber, one of said walls partly defining the first location for the fluent mass, and the other of said walls partly defining the second location for the fluent mass.
13. The mechanism of Claim 12 wherein: the weight means is mounted on the shaft adjacent the first location for the fluent mass.
14. The mechanism of Claim 12 wherein: the fluent mass comprise a plurality of metal members located in the chamber.
15. The mechanism of Claim 1 wherein: the means to selectively rotate the shaft includes a reversible motor drivably connected to the shaft.
16. A drum and vibratory mechanism for a road compacting machine comprising: a generally cylindrical shell having opposite ends, end walls secured to opposite end portions of the shell a shaft located within said shell between said end walls, means rotatably mounting the shalt on said end walls, weight means secured to said shaft, said weight means having an eccentric first mass whereby upon rotation of said shaft said first mass causes the shaft to vibrate, means mounted on the shaft having a fluent second mass which upon rotation of the shaft in one direction moves the fluent second mass to a first location to augment the eccentric distribution of the first mass thereby producing high amplitude vibration of the shaft and shell and upon rotation in the opposite direction said fluent second mass moves to a second location to generally balance the shaft thereby producing low amplitude vibration of the shaft and shell, and means to selectively rotate the shaft in opposite directions.
17. The drum and vibratory mechanisms of Claim 16 wherein: the end walls have central apertures, said means rotatably mounting the shaft comprising housings extended through the apertures, means securing the housings to the end walls, and bearing means mounting opposite ends of the shaft on the housings.
18. The drum of vibratory mechanism of Claim 16 wherein: the weight means comprise a pair of weights mounted on opposite end portions of the shaft, each weight having an eccentric located first mass.
19. The drum and vibratory mechanism of Claim 16 wherein: the means mounted on the shaft having a fluent second mass comprises a casing mounted on the shaft, said casing having a chamber accommodating the fluent second mass, and partion means located in said chamber pro-viding said first and second locations for the fluent second mass.
20. The drum and vibratory mechanism of Claim 16 wherein: the means mounted on the shaft having a fluent second mass comprises a pair of casings secured to opposite end portions of the shaft, each casing having a chamber concentric about the shaft accommodating fluent second mass, and partition means located in each chamber providing said first and second locations for the fluent second mass .
21. The drum and vibratory mechanism of Claim 20 wherein: the weight means comprise a pair of weights mounted on the shaft adjacent the casings, each weight having an eccentric located first mass, said first mass being located adjacent the first locations for the fluent second mass.
22. The drum and vibratory mechanism of Claim 20 wherein: the fluent second mass comprises a plurality of metal members.
23. The drum and vibratory mechanism of Claim 16 wherein: the means mounted on the shaft having a fluent second mass comprises casing means having a chamber for accommodating the fluent second mass, said chamber being concentric with the longitudinal axis of the shaft, and at least one partition means located within the chamber which upon rotation of the shaft confines the fluent second mass to a first chamber portion in which the fluent second mass augments the eccentricity of the weight means and a second chamber portion in which the fluent second mass tends to balance the eccentricity of the weight means.
24. The drum and vibratory mechanism of Claim 23 wherein: said partition means comprises a pair of walls, one of said walls having a first section which extends across the chamber defining part of a chord and a second wall having a section that extends parallel to the chord of the first section.
25. The drum and vibratory mechanism of Claim 16 wherein: the means mounted on the shaft having a fluent second mass comprises a casing means mounted on the shaft, said casing means having a chamber accommodating the fluent second mass, and partition means located in said chamber providing said first and second locations for the fluent second mass, said partition means comprising a pair of walls located in said chamber, one of said walls having a first section which extends from the axle across the chamber defining part of a chord and a second section extended radially from said shaft located generally per-pendicular to the first section, the other wall having a first section which extends from the shaft generally parallel to the chord of the first wall and a second section which is radial with respect to the shaft, said walls lying in the same semi-circle of the chamber, one of said walls partly defining the first location for the fluent second mass, and the other of said walls partly defining the second location for the fluent second mass.
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19843426908 DE3426908A1 (en) | 1984-07-20 | 1984-07-20 | Vibration mechanism |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA1220373A true CA1220373A (en) | 1987-04-14 |
Family
ID=6241208
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA000458390A Expired CA1220373A (en) | 1984-07-20 | 1984-07-06 | Vibratory mechanism |
Country Status (3)
| Country | Link |
|---|---|
| CA (1) | CA1220373A (en) |
| DE (1) | DE3426908A1 (en) |
| SE (1) | SE440194B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105478334A (en) * | 2015-11-11 | 2016-04-13 | 上海大学 | Amplitude-adjustable circumferential oscillation mechanism |
| CN106523594A (en) * | 2016-12-30 | 2017-03-22 | 武汉新华源电力设备有限公司 | Heavy punch cylinder and vibration motor eccentric block assembly |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3078730A (en) * | 1961-01-06 | 1963-02-26 | Bell Intercontinental Corp | Vibratory device and amplitude adjustment means |
| US3722381A (en) * | 1971-04-03 | 1973-03-27 | Vibro Verken Ab | Dual amplitude vibration generator |
| JPS5547935Y2 (en) | 1976-03-29 | 1980-11-10 |
-
1984
- 1984-07-06 CA CA000458390A patent/CA1220373A/en not_active Expired
- 1984-07-18 SE SE8403782A patent/SE440194B/en not_active IP Right Cessation
- 1984-07-20 DE DE19843426908 patent/DE3426908A1/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| DE3426908A1 (en) | 1986-01-30 |
| DE3426908C2 (en) | 1992-09-03 |
| SE440194B (en) | 1985-07-22 |
| SE8403782D0 (en) | 1984-07-18 |
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