EP0960659A1 - Travel control device for vibrating plate compactor - Google Patents
Travel control device for vibrating plate compactor Download PDFInfo
- Publication number
- EP0960659A1 EP0960659A1 EP99108350A EP99108350A EP0960659A1 EP 0960659 A1 EP0960659 A1 EP 0960659A1 EP 99108350 A EP99108350 A EP 99108350A EP 99108350 A EP99108350 A EP 99108350A EP 0960659 A1 EP0960659 A1 EP 0960659A1
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- European Patent Office
- Prior art keywords
- piston
- spool
- cylinder
- passage
- control device
- 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.)
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- 230000007935 neutral effect Effects 0.000 claims description 32
- 230000037431 insertion Effects 0.000 claims description 2
- 238000003780 insertion Methods 0.000 claims description 2
- 238000010276 construction Methods 0.000 description 9
- 238000010586 diagram Methods 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000002950 deficient Effects 0.000 description 1
- 238000007599 discharging Methods 0.000 description 1
- 230000002708 enhancing effect Effects 0.000 description 1
- 238000005192 partition Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000005303 weighing Methods 0.000 description 1
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Classifications
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- 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
- B06B1/166—Where the phase-angle of masses mounted on counter-rotating shafts can be varied, e.g. variation of the vibration phase
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- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
- E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
- E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
- E01C19/30—Tamping or vibrating apparatus other than rollers ; Devices for ramming individual paving elements
- E01C19/34—Power-driven rammers or tampers, e.g. air-hammer impacted shoes for ramming stone-sett paving; Hand-actuated ramming or tamping machines, e.g. tampers with manually hoisted dropping weight
- E01C19/38—Power-driven rammers or tampers, e.g. air-hammer impacted shoes for ramming stone-sett paving; Hand-actuated ramming or tamping machines, e.g. tampers with manually hoisted dropping weight with means specifically for generating vibrations, e.g. vibrating plate compactors, immersion vibrators
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- E—FIXED CONSTRUCTIONS
- E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
- E02D—FOUNDATIONS; EXCAVATIONS; EMBANKMENTS; UNDERGROUND OR UNDERWATER STRUCTURES
- E02D3/00—Improving or preserving soil or rock, e.g. preserving permafrost soil
- E02D3/02—Improving by compacting
- E02D3/046—Improving by compacting by tamping or vibrating, e.g. with auxiliary watering of the soil
- E02D3/074—Vibrating apparatus operating with systems involving rotary unbalanced masses
Definitions
- This invention is related to a travel control device for a vibrating plate compactor used for compacting the paved road surfaces, and more particularly to a travel control device for a vibrating plate compactor wherein the rotational phase of one of the two eccentric rotors rotating on a pair of parallel axes is changed relative to the other eccentric rotor and the compactor is moved forward/backward by the synthesized vector thereof.
- This type vibrating plate compactor generally known in the prior art has a pair of eccentric rotors, the rotational phase of one rotor being variable relative to the other rotor and its vector moving the device forward or backward.
- a device which uses hydraulic pressure to switch the travel direction forward or backward in order to change the rotational phase of an eccentric rotor is known from prior references such as Japanese Patent Kokai Nos. Sho 55/139884, Sho 63/60306, Hei 1/260107, and Hei 7/286306.
- the compactor according to Japanese Patent Kokai Hei 1/260107 is provided with piston rods which can maintain the neutral state by springs on both sides inside the driven shaft, pistons and cylinders on both sides of the piston rod, connecting the cylinders and the outside pressure source to charge the pressure oil to one of the cylinders from the outside source to move the piston rod.
- This compactor is also problematic in that the hand-operated pump used for supplying pressure into respective cylinders requires large force and the switching operation is so heavy that heavy weight compactors cannot be used.
- the compactor according to Japanese Patent Kokai Sho 63/60306 is provided with a piston and a cylinder at one end of the piston rod inside the driven shaft, and the cylinder is connected to a three-way switch valve in the directions of forward, backward and neutral positions and a hydraulic pump circuit to always return these valves to the neutral position by the spring force.
- the pressure of this hydraulic pump is used to supply pressure to the cylinder via the valves on the forward and backward sides.
- the compactor according to Japanese Patent Kokai Hei 7/286306 is similar to the compactor disclosed in Japanese Patent Kokai Hei 1/260107 in that it is provided with a piston rod maintained neutral by springs on both sides in the driven shaft, and pistons and cylinders are respectively provided at both ends of the piston rod.
- a hydraulic pump circuit provided with a three-way valve which can be switched to the forward, backward and neutral directions is connected to both cylinders as an outside source to supply the oil from the valve to respective cylinders in order to switch the piston rod to any one of the three directions.
- the invention aims to offer a novel vibrating plate compactor which can set the travel lever at an arbitrary position between the fastest forward speed and the fastest backward speed for traveling the compactor at a desired speed event when the compactor is heavier than 500 kg by using a hydraulic pump circuit provided with a servo function as an outside pressure source for the piston rod to change the rotational phase of one of the eccentric rotors in a vibrating plate generator.
- the travel control device for the vibrating plate compactor is characterized by the provision of a piston to receive at one end thereof the mechanical return force applied from the direction of the piston rod inside the cylindrical body, and a servo valve mechanism to supply oil from a hydraulic pump outside the body to the other end of the piston to resist the mechanical return force from the direction of the piston rod.
- Said travel control device is preferably provided with a piston at one end of the cylindrical body to receive at one end thereof the mechanical return force from the direction of the said piston rod, a push rod for switching the travel direction between forward and backward directions at the other end of said body, a spool for the servo valve mechanism at the center of the said body to charge oil from the hydraulic pump positioned outside the body to the other end of the piston in order to resist the mechanical return force, and springs respectively between said piston and said push rod.
- a passage for the pressure oil on the side of the vibration generator to guide the oil into the piston as a mechanical return force is applied from the direction of the piston rod of the vibration generator
- another passage on the pump side to supply oil from the hydraulic pump outside the body to the outside of said piston to resist said mechanical return force.
- the body supporting said spool is preferably constructed by providing a first passage to supply oil from the hydraulic pump to the outside of the piston via a concave groove cut on the outer periphery of the spool as the spool travels laterally by operation of the push rod, and a second passage on the tank side to send oil returned from the outside of said piston through said first passage to the tank via another concave groove cut on the outer periphery of the spool.
- the present compactor basically comprises a vibration generator 1 shown in Fig. 1 and a travel control device 20 shown in Fig. 2 provided with a hydraulic servo valve mechanism for switching the direction of thrust generated by the vibration generator 1 to the device to forward or backward directions.
- the vibration generator 1 has a drive shaft 3 to which rotation is transmitted via a pulley 2 from an engine not shown, and a driven shaft 4 which is positioned parallel to the drive shaft 3.
- An eccentric rotor 5 is fixedly mounted on the drive shaft 3 and a similar eccentric rotor 6 is fixed axially to the driven shaft 4 in such a way that the phase may be varied relative to said eccentric rotor 5.
- a driven gear 7 which is rotatable with the shaft 4 and fixed axially to prevent travel in the axial direction.
- the driven gear 7 is transmitted rotation from the drive gear 8 of the drive shaft 3.
- Said driven gear 7 is provided a spiral groove 10 on the inner wall of a boss 9 inclined in respect of the axis of the boss 9.
- Said driven gear 4 is shaped like an open barrel with elongated holes 11 cut on the opposing walls at the position of said driven gear 7 respectively along the axial direction.
- a piston rod 12 is inserted rotatably and movably in the axial direction inside the driven shaft 4.
- the piston rod 12 has a boss 13 of a size to allow sliding inside the driven shaft 4 at one end and a piston 15 at another end via a bearing 16.
- a hydraulic cylinder 18 On the outside of a vibrating case 17 to one end of which is axially fixed the driven shaft 4 is provided a hydraulic cylinder 18 inserted with said piston 15.
- a knock pin 19 to perpendicularly cross the axial direction of the rod 12, and both ends of the knock pin 19 are fit inside the spiral groove 10 on the inner wall of said driven shaft 4 through the elongated hole 11 of said driven shaft 4.
- the hydraulic cylinder 18 inserted with the piston 15 at one end of the piston rod 12 is connected to one end of said travel control device 20 provided outside.
- the device 20 imparts resistance against said mechanical return force inside said hydraulic cylinder 18 by utilizing the pressure oil from an outside hydraulic pump 41, and also functions to push the piston rod 12 to the left (forward) side of Fig. 1 by overcoming said mechanical return force.
- the device 20 is constructed with a push rod 22 inserted through a right chamber 21a at one end of the body 21 to connect the outer end thereof with a travel lever 23, a spool 24 inserted into the central chamber 21b to be moved by the push rod 22, and a piston 29 inserted into the left chamber 21c at the other end to be moved by the spool 24, and is further provided with a passage 45 on the vibration generator side connected to the hydraulic cylinder 18 of the vibration generator 1 inside the center chamber 21b provided with the above mentioned spool 24.
- the inside of the right chamber 21a of the body 2 is shaped like a cylinder 26, and the push rod 22 having a flange 22a at the inside end is inserted slidably therethrough,
- One end of the rod 22 provided with said flange 22a is also shaped like a cylinder 22b,
- a spring bearing 25 having a boss 25a engaged with the flange 22a at the right and a flange 25b abutting upon the inner wall of the center chamber 21b on the left.
- a spring 27 is inserted between the left flange 25b of the spring bearing 25 and the right and of the cylinder 26 inside said right chamber 21a to support said push rod 22 in a neutral position.
- a hydraulic cylinder 28 inside the left chamber 21c of said body 21 provided with a piston 29 inside.
- a rod 30 extending to the right side of the piston 29 is inserted in a freely slidable fashion into a bearing 31 provided on the side of the center chamber 21b of the left chamber 21c.
- the right end of the rod 30 facing the center chamber 21b is shaped as a cylinder 30a inside which is positioned a spring 32 with one end extending into the center chamber 21b.
- a hole 33 connecting the right chamber 21a and the left chamber 21c on the same axis is bored in the center chamber 21b of the body 21, and the spool 24 is slidably positioned inside the hole 33.
- the portion between the flange 34a and the push rod 22 provided on the right hand side outer periphery of the spool 24 is supported by a spring 35 placed inside the cylinder 22b of the push rod 22.
- the portion between the flange 34b provided on the left side outer periphery of the spool 24 and said piston rod 30 is supported by the spring 32 positioned inside the cylinder 30a of said piston rod 30. Therefore, said spool 24 is supported by a uniform spring pressure at the prescribed center position of the center chamber 21b by the left spring 32 and the right spring 35.
- the length of the hole 33 inside the center chamber 21b for inserting the spool is slightly shorter than the distance between the flanges 34a and 34b provided on the left and the right outer peripheries of the spool 24, so that when the spool 24 is maintained at the prescribed center position of the center chamber 21b by the springs 32 and 35 on both sides, a short concave portion 37 is created with an interstice 36a between the right end of the hole 33 and the right flange 34a of the spool 24.
- a long concave portion 38 with the interstice 36b to allow entry of the right end of said piston rod 30 is provided between the left end of the hole 33 and the left flange 34b of the spool 24 a long concave portion 38 with the interstice 36b to allow entry of the right end of said piston rod 30.
- a pair of concave grooves 39, 40 are provided with a prescribed interval at the center of said spool 24.
- a passage 42 connecting to a pump side port P of said hydraulic pump 41 and extending from the side of the center chamber 21b toward the hole 33 at a concave groove 39 on the right.
- a passage 45 on the vibration generator side connecting with the hydraulic cylinder 18 of the piston rod 12 in said vibration generator 1, the passage being parallel to the pump side circuit 42 connecting with the pump side port P of the hydraulic pump 41.
- another passage 46 for oil pressure provided with a check valve 47 leading to the right side of the piston 29 in the hydraulic cylinder 28 through the left chamber 21c from the center chamber 21b.
- the numeral 48 in Fig. 4 denotes a relief valve for discharging the air mixed in the hydraulic cylinder 18 of the piston rod 12 in said vibration generator 1.
- the lever 23 of the travel control device 20 When using a compactor as constructed above by maintaining the compactor in a neutral position, the lever 23 of the travel control device 20 is kept neutral as shown in Fig. 2.
- the spool 24 of the device 20 is supported at the center of the center chamber 21b by the spring pressure of the springs 32, 35 on the left and the right sides, and the passage 43 for supplying pressure to the left side of the piston 29 in the hydraulic cylinder 28 is between the concave grooves 39, 40 on the left and the right of the spool 24.
- the pump side passage 42 is therefore closed.
- the push rod 22 on the right side of the spool 24 receives the spring pressure toward right by the spring 35, but the spring pressure at the springs 27 and 35 attains an equilibrium because of the spring pressure toward left by the outside spring 27 of the outside spring bearing 25.
- the device maintains its neutral state even when the operator removes his/her hands from the lever 23 connected to the push rod 22.
- the piston rod 12 of the vibrating plate generator 1 shown in Fig. 1 is positioned at the center of the driven shaft 4 at this time, but as the driven gear 7 continues its rotation, mechanical return force is imparted to the piston rod 12 toward the right hand side.
- the pressure oil inside the hydraulic cylinder 18 of the vibration generator 1 passes through, the passage 45 on the side of the generator in the center chamber 21b of the device 20 and the passage 46 for oil pressure and flows to the right hand side of the piston 29 inside the hydraulic cylinder 28, to thereby push the piston 29 toward the left side of the hydraulic cylinder 28 from the position shown in Fig. 2.
- the pump side passage 42 again becomes positioned at the intermediate position of the left and the right concave grooves 39, 40 as shown in Fig. 2, and blocks the flow of pressure oil from the pump side passage 42 to the left side of the piston 29 via the passage 43 for pressure oil.
- Oil from the passage 45 on the vibration generator side again flows through the passage 46 into the right hand side of the piston 29 to push the piston 29 back to the left side.
- the lever 23 When moving the device from the neutral to the forward position, the lever 23 should be pushed until it reaches the fastest forward position in the left at the figure or be maintained at an arbitrary position for setting the speed between the neutral and the fastest forward positions.
- the device advances at a prescribed speed corresponding to the angle of inclination of the lever 23.
- the device advances as described above, but the spool 24 repeats the above mentioned lateral movement corresponding to the intensity of the force of the spring 35 which pushes the push rod 22 to the left.
- This increases the oil amount on the left rather than on the right of the piston 29 inside the cylinder 28, and this status is transmitted to the cylinder 18 of the generator 1 from the passage 45, to thereby advance the device at a predetermined speed.
- the lever 7 When the device is moved backward, the lever 7 is pulled to the fastest backward speed position to the right of the figure from the neutral position as shown in Fig. 7, or maintained at an arbitrary angle between the neutral position and the fastest backward speed.
- the push rod 22 is pulled to the right by resisting the pressure of the spring 27 on the outer periphery of the spring bearing 25 as shown in Fig. 7, and the spring force of the right spring 35 becomes lowered.
- This moves the spool 24 to the right and connects the left concave groove 40 with the passage 43, which is at this time cut from the pump side passage 42. Since the left groove 40 is connected with the tank side passage 44 leading to the port T on the tank side, the oil on the left of the piston 29 is discharged toward the tank from the passage 43 via the concave groove 40 and the passage 44 on the tank side.
- the device When the lever 23 is held at an arbitrary position before reaching the fastest backward speed position, the device recedes at a prescribed speed corresponding to the angle of inclination of the lever 23.
- Figs. 9 through 14 show another construction of a travel control device 50 according to the second embodiment of the present invention
- the device 50 consists of a piston 66 placed inside a cylinder 58 comprising a body 51, a push rod 52 manipulated by an outside travel lever 53 inserted into the left chamber 58a of the cylinder 58, and a spool 59 positioned in such a way to be inserted into the left side of the piston 66.
- a passage 90 connecting with the hydraulic cylinder 18 of the vibration generator 1.
- a passage 60 on the pump side to connect with a hydraulic pump 55 and a passage 61 on the tank side.
- Said piston 66 is provided with an elongated hole 63 along its axis at the right end thereof, through which is inserted a vertical barrel 65 crossing perpendicular with the axis of the piston 66.
- the piston 66 therefore moves laterally along the length of the elongated hole 63 without revolving inside the body 51.
- the vertical barrel 65 has orifices 64a, 64b and is connected at its top with the tank side passage 61.
- a spring 62 Inside the right chamber 58b of the cylinder between the right end of the piston 66 and a plug 56 closing the right end of the body 51.
- a long concave groove 68 to receive the oil from the pump side passage 60 of said hydraulic pump 55, an orifice 69 at the left end of the groove 68 to guide the oil from the groove 68 toward the outer periphery of the inner spool 59, and a short concave groove 70 on the inner periphery of the piston 66 on the right side spaced slightly apart from the orifice 69.
- the above mentioned left section 66a of the piston has an orifice 75 on the right wall 71 and a short concave portion 84 having an inner diameter to allow insertion of a flange 86 between the push rod 52 and the spool 59 at the left end.
- the spool 59 is provided at the end of the push rod 52 inserted into the left chamber 58a through the plug 57 closing the left end of the body 51, and is placed inside a cylindrical chamber 67 within the left section 66a of the piston.
- spring 72 is provided between the right end of the spool 59 in the chamber 67 and the right wall 71 of the left section 66a of the piston to impart the force to the spool 59 to constantly push to the left.
- a pin 74 is fixed to the piston 66 at both ends of the hole to cross the axis of the spool 59 perpendicularly, The pin 74 stops the spool 59 from slipping ant of the left section 66a.
- a partition wall 76 to divide the inside of the spool 59 into passages 77, 78.
- a concave groove 79 is cut on the outer periphery of the spool 59 on the left side of the wall 76 and a concave groove 80 on the outer periphery of the spool 59 on the right side of the wall 76.
- an orifice 81 to connect the groove 70 on the inner periphery of the left section 66a of the piston and the left passage 77 inside the spool 59.
- An orifice 82 is provided on the groove 80 on the outer periphery of the spool 59 connecting with the chamber 78 on the right side of the wall 76 in the spool 59.
- an orifice 83 connecting with the left chamber 58a of the cylinder on the left side of the piston 59 by passing through a flange 86 between the push rod 52 and the spool 59.
- valve 85 is closed when the piston 66 and the spool 59 travel to the right in the body 51 as shown in Figs. 9 and 12, but when the piston 66 moves to the farthest left inside the body 51, it contacts said vertical barrel 65 and opens to release a part of the pressure oil in the right chamber 58b of the cylinder to the tank side passage 61 from the barrel 65.
- the travel lever 53 is set at the neutral position as shown in Fig. 9 when the device is to be maintained in the neutral state, and the position is held manually,
- the piston 66 is positioned at the intermediate point of the cylinder 58 at this time, In this state, the pressure oil receiving the mechanical return force of the vibration generator 1 is charged into the right chamber 58b of the cylinder on the right side of the body 51 through the passage 90.
- the piston 66 moves to the left by the pressure oil and the spring 62 as shown in Fig. 10, opens the circuit to charge the oil from the passage 60 on the pump side of the hydraulic pump 55 to the left of the piston 66, and the pressure increases inside the left chamber 58a of the cylinder.
- the piston 66 is therefore pushed back to the right as shown in Fig. 11.
- the oil from the left chamber 58a of the cylinder passes through the spool 59 to the tank side passage 61 of the hydraulic pump 55 from the barrel 65 and lowers the pressure inside the left chamber 58a on the left of the piston 66.
- the piston 66 is then pushed again toward the left by the oil charged into the right chamber 58b of the cylinder and the force of spring 62 as shown in Fig. 10.
- the travel lever 53 When the device is to be moved forward from the neutral position, the travel lever 53 is pushed until the fastest forward position on the left side of the figure is reached or is maintained at an arbitrary angle for setting the speed prior to that position.
- the piston 66 repeats the lateral movement as described above at the position with the spool 59 standing still at the end of the push rod 52.
- the travel lever 53 When the device is brought backward from the neutral position, the travel lever 53 is pushed to the fastest backward speed position on the left side of the figure as shown in Fig. 13, or is maintained at an arbitrary angle for setting the speed prior to that position.
- the spool 59 is pulled toward the left by the push rod 52, or the circuit to charge the oil from the left chamber 58b of the cylinder at the left of the piston 66 to the tank side passage 61 of the hydraulic pump 55 opens and the oil charged from the vibration generator 1 through the passage 90 increases the pressure inside the right chamber 58b of the cylinder on the right side of the piston 66.
- the piston 66 is pushed back to the left as in Fig. 10, but since the push rod 52 is being pulled toward the backward direction (to the left) by the travel lever 53, the spool 59 immediately moves to the left as shown in Fig.
- the piston 66 repeats the lateral movement as described above with the spool 59 standing stationary at the end of the push rod 52, to bring the device backward at the prescribed speed.
- the travel control device for the vibrating plate compactor is provided with a piston to receive the mechanical return force from the vibration generator in the cylindrical body on one hand, and a servo valve spool which can supply the pressure from the hydraulic pump to resist the mechanical return force acting on the piston by manipulating the push rod on the other, so that the device can supply the pressure to one side of the piston from the hydraulic pump to resist the powerful mechanical return force from the vibration generator even when the compactor is very large with its weight exceeding 500 kg, and the switching operation of the travel lever may be made lighter, It is also possible to control the speed at any position in the forward or backward directions with the travel lever in operation.
- the construction of the first embodiment provides a spool between the piston and the push rod via a spring in order to enable transmission of the force to operate the push rod to the spool via a spring and to further make the switching operation of the travel lever lighter.
- the travel lever maintains its neutral condition automatically, thus enhancing safety by eliminating any risks of the device running out of control.
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Abstract
Description
- This invention is related to a travel control device for a vibrating plate compactor used for compacting the paved road surfaces, and more particularly to a travel control device for a vibrating plate compactor wherein the rotational phase of one of the two eccentric rotors rotating on a pair of parallel axes is changed relative to the other eccentric rotor and the compactor is moved forward/backward by the synthesized vector thereof.
- This type vibrating plate compactor generally known in the prior art has a pair of eccentric rotors, the rotational phase of one rotor being variable relative to the other rotor and its vector moving the device forward or backward. A device which uses hydraulic pressure to switch the travel direction forward or backward in order to change the rotational phase of an eccentric rotor is known from prior references such as Japanese Patent Kokai Nos. Sho 55/139884,
Sho 63/60306, Hei 1/260107, and Hei 7/286306. - These known compactors are all provided with a spiral groove inside the driven gear on the driven shaft which is rotated by the drive shaft, and a piston rod having a pin to engage with the spiral groove of said driven gear inside said driven shaft. Common to these devices is the way in which the driven gear having the spiral groove is rotated by moving the piston rod in the axial direction and varying the rotational phase of the eccentric rotor on the driven shaft relative to the eccentric rotor on the drive shaft.
- Among such compactors, that at Japanese Patent Kokai Sho 55/139884 is provided with a cylindrical driven gear and a piston rod and imparted the mechanical return force moving to one side of the cylindrical driven shaft on the piston rod by synthetic thrust of the rotor on the driven shaft and the rotor on the drive shaft imparts. The hydraulic pressure resisting the mechanical return force of the piston rod is applied from an outside source into the cylinder provided at one end of the cylindrical driven shaft, and by variably controlling the hydraulic pressure supplied, the position of the rotational angle of the driven gear can be selected to suitably change the phase of the eccentric rotor.
- However, since a hand-held pump is used as a means to supply the oil into the cylinder provided at one end of the cylindrical driven shaft from the outside source to resist the mechanical return force trying to move toward one side of the cylinder of the piston rod in this conventional compactor, this type device requires large force to manually switch the pump to the opposite side from the position of the piston rod traveling with the fastest speed forward or backward against the largest mechanical return force. In large, heavy weight compactors, the switching operation becomes so heavy that it is impossible to operate the machine.
- The compactor according to Japanese Patent Kokai Hei 1/260107 is provided with piston rods which can maintain the neutral state by springs on both sides inside the driven shaft, pistons and cylinders on both sides of the piston rod, connecting the cylinders and the outside pressure source to charge the pressure oil to one of the cylinders from the outside source to move the piston rod. This compactor is also problematic in that the hand-operated pump used for supplying pressure into respective cylinders requires large force and the switching operation is so heavy that heavy weight compactors cannot be used.
- On the other hand, the compactor according to Japanese Patent Kokai Sho 63/60306 is provided with a piston and a cylinder at one end of the piston rod inside the driven shaft, and the cylinder is connected to a three-way switch valve in the directions of forward, backward and neutral positions and a hydraulic pump circuit to always return these valves to the neutral position by the spring force. The pressure of this hydraulic pump is used to supply pressure to the cylinder via the valves on the forward and backward sides. While this compactor is advantageous in that the switching operation requires small force and the speed can be controlled by the pressure oil charged to the cylinder at one end of the piston rod by the hydraulic pump, it is quite defective in that the switch valve always returns to the neutral position by the spring force. It is therefore impossible to hold the travel lever at a desired inclined position.
- The compactor according to Japanese Patent Kokai Hei 7/286306 is similar to the compactor disclosed in Japanese Patent Kokai Hei 1/260107 in that it is provided with a piston rod maintained neutral by springs on both sides in the driven shaft, and pistons and cylinders are respectively provided at both ends of the piston rod. A hydraulic pump circuit provided with a three-way valve which can be switched to the forward, backward and neutral directions is connected to both cylinders as an outside source to supply the oil from the valve to respective cylinders in order to switch the piston rod to any one of the three directions.
- Although this compactor can reduce the force needed for switching because oil is supplied to cylinders at both ends of the piston rod by the hydraulic pump, all the oil from the pump is fed by switching the valve to the forward or backward directions to thereby set the fastest running speed in these directions. It is therefore impossible to set the running speed at an arbitrary speed.
- This invention was contrived in view of the problems discussed above in the conventional type vibrating plate compactors. More concretely, the invention aims to offer a novel vibrating plate compactor which can set the travel lever at an arbitrary position between the fastest forward speed and the fastest backward speed for traveling the compactor at a desired speed event when the compactor is heavier than 500 kg by using a hydraulic pump circuit provided with a servo function as an outside pressure source for the piston rod to change the rotational phase of one of the eccentric rotors in a vibrating plate generator.
- In a vibrating plate compactor provided with an eccentric rotor on one of the two parallel axes connected to each other of which rotor can vary the rotational phase of the eccentric rotor on the other axis, a piston rod inserted slidably into the shaft of the eccentric rotor for changing the phase of said eccentric rotor, and a vibration generator having a hydraulic cylinder at one end of the axis of the piston rod to switch the rotation of rotors in the forward and backward directions by moving the piston rod axially by the hydraulic pressure resisting the mechanical return force generated by the rotation of the eccentric rotor, the travel control device for the vibrating plate compactor according to the present invention is characterized by the provision of a piston to receive at one end thereof the mechanical return force applied from the direction of the piston rod inside the cylindrical body, and a servo valve mechanism to supply oil from a hydraulic pump outside the body to the other end of the piston to resist the mechanical return force from the direction of the piston rod.
- Said travel control device is preferably provided with a piston at one end of the cylindrical body to receive at one end thereof the mechanical return force from the direction of the said piston rod, a push rod for switching the travel direction between forward and backward directions at the other end of said body, a spool for the servo valve mechanism at the center of the said body to charge oil from the hydraulic pump positioned outside the body to the other end of the piston in order to resist the mechanical return force, and springs respectively between said piston and said push rod.
- Between the spool at the center of the body and the inside of the piston is provided a passage for the pressure oil on the side of the vibration generator to guide the oil into the piston as a mechanical return force is applied from the direction of the piston rod of the vibration generator, and between said spool and the outside of the piston is provided another passage on the pump side to supply oil from the hydraulic pump outside the body to the outside of said piston to resist said mechanical return force.
- The body supporting said spool is preferably constructed by providing a first passage to supply oil from the hydraulic pump to the outside of the piston via a concave groove cut on the outer periphery of the spool as the spool travels laterally by operation of the push rod, and a second passage on the tank side to send oil returned from the outside of said piston through said first passage to the tank via another concave groove cut on the outer periphery of the spool.
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- Fig. 1 is a sectional view to show the construction of a vibration generator in, the vibrating plate compactor according to the present invention;
- Fig. 2 is a sectional view to show the construction of the travel control device in the vibrating plate compactor according to the present invention;
- Fig. 3 is an enlarged sectional view of the center portion of Fig. 1;
- Fig. 4 is a sectional view along the line IV-IV in Fig. 2;
- Fig. 5 is a sectional view of the travel control device in a neutral position with the circuit on the pump side open;
- Fig. 6 is a sectional view showing the travel control device at its fastest forward speed;
- Fig. 7 is a sectional view showing the travel control device at its fastest backward speed;
- Fig. 8 is a hydraulic circuit diagram of the travel control device;
- Fig. 9 is a sectional view showing construction of another embodiment of the travel control device;
- Fig. 10 is a sectional view showing the travel control device of Fig. 9 in a neutral position with the circuit on the pump side open.
- Fig. 11 is a sectional view showing the circuit on the tank side open;
- Fig. 12 is a sectional view showing the travel control device of Fig. 9 at its fastest forward speed;
- Fig. 13 is a sectional view showing the travel control device of Fig. 9 at its fastest backward speed;
- Fig. 14 is a sectional view showing the hydraulic circuit diagram for the travel control device shown in Fig. 9.
-
- Referring to embodiments of the vibrating plate compactor according to the present invention as shown in the attached drawings, the present compactor basically comprises a
vibration generator 1 shown in Fig. 1 and atravel control device 20 shown in Fig. 2 provided with a hydraulic servo valve mechanism for switching the direction of thrust generated by thevibration generator 1 to the device to forward or backward directions. - As shown in Fig. 1, the
vibration generator 1 has adrive shaft 3 to which rotation is transmitted via apulley 2 from an engine not shown, and a drivenshaft 4 which is positioned parallel to thedrive shaft 3. Aneccentric rotor 5 is fixedly mounted on thedrive shaft 3 and a similareccentric rotor 6 is fixed axially to the drivenshaft 4 in such a way that the phase may be varied relative to saideccentric rotor 5. - At the center of the driven
shaft 4 is provided a drivengear 7 which is rotatable with theshaft 4 and fixed axially to prevent travel in the axial direction. The drivengear 7 is transmitted rotation from the drive gear 8 of thedrive shaft 3. Said drivengear 7 is provided aspiral groove 10 on the inner wall of a boss 9 inclined in respect of the axis of the boss 9. - Said driven
gear 4 is shaped like an open barrel withelongated holes 11 cut on the opposing walls at the position of said drivengear 7 respectively along the axial direction. Apiston rod 12 is inserted rotatably and movably in the axial direction inside the drivenshaft 4. - The
piston rod 12 has aboss 13 of a size to allow sliding inside the drivenshaft 4 at one end and apiston 15 at another end via abearing 16. On the outside of a vibratingcase 17 to one end of which is axially fixed the drivenshaft 4 is provided ahydraulic cylinder 18 inserted with saidpiston 15. - In the
boss 13 of thepiston rod 12 is embedded aknock pin 19 to perpendicularly cross the axial direction of therod 12, and both ends of theknock pin 19 are fit inside thespiral groove 10 on the inner wall of said drivenshaft 4 through theelongated hole 11 of said drivenshaft 4. - When rotation from the drive gear 8 is transmitted to the driven
gear 7 with zero hydraulic pressure on thehydraulic cylinder 18 inserted with thepiston 15 at one end of thepiston rod 12, mechanical return force being pushed toward the right side of Fig. 1 is imparted to thepiston rod 12 since both ends of thepin 19 are engaged with thespiral groove 10 on the inner wall of said drivenshaft 4 through theelongated holes 11 of the drivengear 4 in the directions of incline of thespiral groove 10 and rotation of the drivengear 7. When thepiston rod 12 moves toward the extreme right in the figure, theeccentric rotor 6 of the drivenshaft 4 is rotated, for instance, to the positional phase either forward or backward relative to theeccentric rotor 5 of the drivenshaft 4. - On the other hand, the
hydraulic cylinder 18 inserted with thepiston 15 at one end of thepiston rod 12 is connected to one end of saidtravel control device 20 provided outside. When thepiston rod 12 inside the drivenshaft 4 receives mechanical return force to the right hand side by thespiral groove 10 of the drivengear 7 as shown in Fig. 2, thedevice 20 imparts resistance against said mechanical return force inside saidhydraulic cylinder 18 by utilizing the pressure oil from an outsidehydraulic pump 41, and also functions to push thepiston rod 12 to the left (forward) side of Fig. 1 by overcoming said mechanical return force. - As shown in Figs. 2 through 7, the
device 20 is constructed with apush rod 22 inserted through aright chamber 21a at one end of thebody 21 to connect the outer end thereof with atravel lever 23, aspool 24 inserted into thecentral chamber 21b to be moved by thepush rod 22, and apiston 29 inserted into theleft chamber 21c at the other end to be moved by thespool 24, and is further provided with apassage 45 on the vibration generator side connected to thehydraulic cylinder 18 of thevibration generator 1 inside thecenter chamber 21b provided with the above mentionedspool 24. - As shown in Figs. 2 and 3, the inside of the
right chamber 21a of thebody 2 is shaped like acylinder 26, and thepush rod 22 having aflange 22a at the inside end is inserted slidably therethrough, One end of therod 22 provided with saidflange 22a is also shaped like acylinder 22b, Over the outer periphery on the left side of saidpush rod 22 are inserted a spring bearing 25 having aboss 25a engaged with theflange 22a at the right and aflange 25b abutting upon the inner wall of thecenter chamber 21b on the left. Between theleft flange 25b of the spring bearing 25 and the right and of thecylinder 26 inside saidright chamber 21a is inserted aspring 27 to support saidpush rod 22 in a neutral position. - There is provided a
hydraulic cylinder 28 inside theleft chamber 21c of saidbody 21 provided with apiston 29 inside. Arod 30 extending to the right side of thepiston 29 is inserted in a freely slidable fashion into abearing 31 provided on the side of thecenter chamber 21b of theleft chamber 21c. The right end of therod 30 facing thecenter chamber 21b is shaped as acylinder 30a inside which is positioned aspring 32 with one end extending into thecenter chamber 21b. - On the other hand, a
hole 33 connecting theright chamber 21a and theleft chamber 21c on the same axis is bored in thecenter chamber 21b of thebody 21, and thespool 24 is slidably positioned inside thehole 33. The portion between theflange 34a and thepush rod 22 provided on the right hand side outer periphery of thespool 24 is supported by aspring 35 placed inside thecylinder 22b of thepush rod 22. The portion between theflange 34b provided on the left side outer periphery of thespool 24 and saidpiston rod 30 is supported by thespring 32 positioned inside thecylinder 30a of saidpiston rod 30. Therefore, saidspool 24 is supported by a uniform spring pressure at the prescribed center position of thecenter chamber 21b by theleft spring 32 and theright spring 35. - As shown in Fig. 3, the length of the
hole 33 inside thecenter chamber 21b for inserting the spool is slightly shorter than the distance between theflanges spool 24, so that when thespool 24 is maintained at the prescribed center position of thecenter chamber 21b by thesprings concave portion 37 is created with aninterstice 36a between the right end of thehole 33 and theright flange 34a of thespool 24. Between the left end of thehole 33 and theleft flange 34b of thespool 24 is provided a longconcave portion 38 with theinterstice 36b to allow entry of the right end of saidpiston rod 30. - A pair of
concave grooves spool 24. Inside thehole 33 of thecenter chamber 21b inserted with thespool 24 is provided apassage 44 on the tank side connecting with a port T on the tank side of saidhydraulic pump 41 positioned outside thebody 21 at the position connecting with theleft groove 40 of thespool 24. In saidhole 33 is provided apassage 43 for oil pressure connecting thecenter chamber 21b to the left side of thepiston 29 in thehydraulic cylinder 28 of theleft chamber 21c at the center of theconcave grooves spool 24. - As shown in Fig. 4, but not in Figs. 2 and 3, on the side of the pump is provided a
passage 42 connecting to a pump side port P of saidhydraulic pump 41 and extending from the side of thecenter chamber 21b toward thehole 33 at aconcave groove 39 on the right. - As also shown in Fig. 4, there is provided at another part of the side of the
center chamber 21b apassage 45 on the vibration generator side connecting with thehydraulic cylinder 18 of thepiston rod 12 in saidvibration generator 1, the passage being parallel to thepump side circuit 42 connecting with the pump side port P of thehydraulic pump 41. At the tip of thepassage 45 is anotherpassage 46 for oil pressure provided with acheck valve 47 leading to the right side of thepiston 29 in thehydraulic cylinder 28 through theleft chamber 21c from thecenter chamber 21b. - The numeral 48 in Fig. 4 denotes a relief valve for discharging the air mixed in the
hydraulic cylinder 18 of thepiston rod 12 in saidvibration generator 1. - When using a compactor as constructed above by maintaining the compactor in a neutral position, the
lever 23 of thetravel control device 20 is kept neutral as shown in Fig. 2. In this state, thespool 24 of thedevice 20 is supported at the center of thecenter chamber 21b by the spring pressure of thesprings passage 43 for supplying pressure to the left side of thepiston 29 in thehydraulic cylinder 28 is between theconcave grooves spool 24. Thepump side passage 42 is therefore closed. Thepush rod 22 on the right side of thespool 24 receives the spring pressure toward right by thespring 35, but the spring pressure at thesprings outside spring 27 of theoutside spring bearing 25. Thus, the device maintains its neutral state even when the operator removes his/her hands from thelever 23 connected to thepush rod 22. - The
piston rod 12 of the vibratingplate generator 1 shown in Fig. 1 is positioned at the center of the drivenshaft 4 at this time, but as the drivengear 7 continues its rotation, mechanical return force is imparted to thepiston rod 12 toward the right hand side. As a result, the pressure oil inside thehydraulic cylinder 18 of thevibration generator 1 passes through, thepassage 45 on the side of the generator in thecenter chamber 21b of thedevice 20 and thepassage 46 for oil pressure and flows to the right hand side of thepiston 29 inside thehydraulic cylinder 28, to thereby push thepiston 29 toward the left side of thehydraulic cylinder 28 from the position shown in Fig. 2. - When the
piston 29 is pushed to the left, the spring pressure of theleft spring 32 of thespool 24 becomes loosened, and thespool 24 moves toward the left by the spring pressure of theright spring 35. This movement of thespool 24 to the left is only for a short distance as theflange 34a on the right of thespool 24 abuts upon the edge of the shortconcave portion 37 at the right edge of thehole 33. - When the
spool 24 moves toward left, theconcave groove 39 connecting to thepassage 42 on the right of the outer peripheral surface of thespool 24 becomes connected to thepassage 43 connecting with the left side of thepiston 29 of thehydraulic cylinder 28 to charge the oil from thepump side passage 42 of thehydraulic pump 41 to the left side of thepiston 29 inside thehydraulic cylinder 28. As the oil amount gradually increases, the pressure on the left side of thepiston 29 overcomes the force from the direction of thehydraulic cylinder 18 of saidvibration generator 1 to push thepiston 29 to the left, and pushes back thepiston 29 to the right, Theleft spring 32 thus moves thespool 24 to the right, This move of thespool 24 to the right is only for a short distance as theflange 34b on the left side of thespool 24 abuts upon the end of theconcave portion 38 of thehole 33. - When the
spool 24 travels to the right, thepump side passage 42 again becomes positioned at the intermediate position of the left and the rightconcave grooves pump side passage 42 to the left side of thepiston 29 via thepassage 43 for pressure oil. Oil from thepassage 45 on the vibration generator side again flows through thepassage 46 into the right hand side of thepiston 29 to push thepiston 29 back to the left side. - As a result of the above operation, when the
lever 23 is set at a neutral position, thepiston 29 is pushed toward the left in thehydraulic cylinder 28 by the mechanical return force from thepassage 45 on the vibration generator side. As shown in Fig. 5, thespool 24 moves leftward and opens thepump side passage 42, and then thepiston 29 is pushed back to the right by the oil from thepassage 42. As shown in Fig. 2, thespool 24 then travels to the right to close thepassage 42, and to push thepiston 29 toward left by the mechanical return force from thepassage 45. This movement is repeated automatically. - In this large-sized compactor weighing more than 500 kg, even if the powerful mechanical return force corresponding to the heavy weight from the
vibration generator 1 pushes thepiston 29 toward the left when operating thelever 23, thepump side passage 42 opens in the next instant to resist the mechanical return force. - Such movement of the
piston 29 takes place at the center of thecylinder 28 as shown in Figs. 2 and 5, and the pressure at the right of thepiston 29 in thecylinder 28 is transmitted to thehydraulic cylinder 18 of thevibration generator 1 from thepassage 45 to position thepiston 15 of thepiston rod 12 at the center of thehydraulic cylinder 18. This maintains the body in a neutral position. As shown in Figs. 2 and 5, thepush rod 22 is standing still at a position to maintain neutrality by thespring 27 outside of thespring bearing 25, so that it is not necessary to manually keep thelever 23 in the prescribed position in order to maintain the device in its safe and neutral position even when the operator removes his/her hand from thelever 23. - When moving the device from the neutral to the forward position, the
lever 23 should be pushed until it reaches the fastest forward position in the left at the figure or be maintained at an arbitrary position for setting the speed between the neutral and the fastest forward positions. - When the
lever 23 is kept pushing from the neutral position to the fastest forward position on the left side, thespool 24 is pushed to the left in the figure by thepush rod 22, so that thepump side passage 42 opens thepassage 43 and pushes thepiston 29 to the right as shown in Fig. 6. As a result, thespool 24 is pushed to the right by thespring 32 and thepassage 43 is closed by thepassage 42 as shown in Fig. 2 and the pressure oil from thepassage 45 on the vibration generator side flows to the right of thepiston 29 inside thehydraulic cylinder 28. - Even when the oil from the
passage 45 flows to the right side of thepiston 29 inside thecylinder 28, the oil on the left side of thepiston 29 stays as shown in Fig. 2 because thepassage 43 is closed by thepump side passage 42 positioned midway of the twogrooves piston 29 stays stationery because of the equilibrium reached by both sides. At this time, thelever 23 keeps pushing thepush rod 22 to the left, and thespool 24 moves immediately to the left as shown in Fig. 6 to open thepassage 42 on the side of the pump. Thespool 24 repeats lateral movements while being pushed to the left by thepush rod 22, to thereby increase the oil amount at the left side of thepiston 29 in the cylinder and to move thepiston 29 gradually to the left as shown in Fig. 6. - Such movement of the
piston 29 takes place in the space to the right of the center of thecylinder 28, and as the pressure on the right side of thepiston 29 in thecylinder 28 is transmitted from thepassage 45 on the vibration generator side to thehydraulic cylinder 18 of thevibration generator 1, thepiston 15 of thepiston rod 12 moves to the left of saidhydraulic cylinder 18 while resisting the mechanical return force to thereby advance the body of the device forward. Finally, the right end of thepiston 29 moves to a position to abut upon the right edge of theleft chamber 21c to achieve the fastest forward speed. - When the
lever 23 is maintained at an arbitrary position before the fastest forward speed position, the device advances at a prescribed speed corresponding to the angle of inclination of thelever 23. - In other words, while the
spring 35 on the right of thespool 24 is being pushed to the left by thepush rod 22 by a prescribed force, the device advances as described above, but thespool 24 repeats the above mentioned lateral movement corresponding to the intensity of the force of thespring 35 which pushes thepush rod 22 to the left. This increases the oil amount on the left rather than on the right of thepiston 29 inside thecylinder 28, and this status is transmitted to thecylinder 18 of thegenerator 1 from thepassage 45, to thereby advance the device at a predetermined speed. - When the device is moved backward, the
lever 7 is pulled to the fastest backward speed position to the right of the figure from the neutral position as shown in Fig. 7, or maintained at an arbitrary angle between the neutral position and the fastest backward speed. - If the
lever 23 is pulled from the neutral position to the fastest backward speed position on the right, thepush rod 22 is pulled to the right by resisting the pressure of thespring 27 on the outer periphery of thespring bearing 25 as shown in Fig. 7, and the spring force of theright spring 35 becomes lowered. This moves thespool 24 to the right and connects the leftconcave groove 40 with thepassage 43, which is at this time cut from thepump side passage 42. Since theleft groove 40 is connected with thetank side passage 44 leading to the port T on the tank side, the oil on the left of thepiston 29 is discharged toward the tank from thepassage 43 via theconcave groove 40 and thepassage 44 on the tank side. - When the oil on the left side of the
piston 29 is discharged into thepassage 44 on the tank side, the oil is supplied to the right side of thepiston 29 from thepassage 45 to push thepiston 29 back to the left. This lowers the force of thespring 32 on the left of thespool 24 and moves thespool 24 to the left as shown in Fig. 2. Thepassage 43 is then closed to cut the flow to thetank side passage 44 and to stop thepiston 29 by equilibrium achieved by pressure oil on both sides. - When the
push rod 22 is kept pulling to the right, the force of thespring 35 on the right of thespool 24 becomes lowered and thespool 24 again moves to the right, theleft groove 40 is connected with thepassage 43, and the oil on the left of thepiston 29 is discharged toward the tank from thegroove 40 via thepassage 44. As the oil flows into the right side of thepiston 29 from thepassage 45, the travel of thepiston 29 and thespool 24 to the left to cut off the flow of the oil from thepassage 45 is repeated. Thepiston 29 gradually moves to a position abutting upon the left end of theleft chamber 21c to achieve the fastest backward speed. - When the
lever 23 is held at an arbitrary position before reaching the fastest backward speed position, the device recedes at a prescribed speed corresponding to the angle of inclination of thelever 23. - In this state, the
push rod 22 is pulled to the right and the force of thespring 35 on the right of the spool is lowered to cause the device, recedes as discussed above. But thespool 24 repeats the above mentioned lateral movement corresponding to the intensity of the force of thespring 35 while thepush rod 22 is pulled to the right. This increases the oil amount an the right side compared to that on the left side of thepiston 29 in thecylinder 28, and this state is transmitted to thehydraulic cylinder 18 of thevibration generator 1 from thepassage 45 to move the device backward while maintaining a prescribed speed. - Figs. 9 through 14 show another construction of a
travel control device 50 according to the second embodiment of the present invention, Thedevice 50 consists of apiston 66 placed inside acylinder 58 comprising abody 51, apush rod 52 manipulated by anoutside travel lever 53 inserted into theleft chamber 58a of thecylinder 58, and aspool 59 positioned in such a way to be inserted into the left side of thepiston 66. In theright chamber 58b of thecylinder 58 on the right side of thebody 51 is apassage 90 connecting with thehydraulic cylinder 18 of thevibration generator 1. At the center of thebody 51 are apassage 60 on the pump side to connect with ahydraulic pump 55 and apassage 61 on the tank side. - Said
piston 66 is provided with anelongated hole 63 along its axis at the right end thereof, through which is inserted avertical barrel 65 crossing perpendicular with the axis of thepiston 66. Thepiston 66 therefore moves laterally along the length of theelongated hole 63 without revolving inside thebody 51. Thevertical barrel 65 hasorifices tank side passage 61. Inside theright chamber 58b of the cylinder between the right end of thepiston 66 and aplug 56 closing the right end of thebody 51 is positioned aspring 62. - As shown in Fig. 10, on the outer periphery of the
left section 66a separated from theelongated hole 63 of saidpiston 66 are provided a longconcave groove 68 to receive the oil from thepump side passage 60 of saidhydraulic pump 55, anorifice 69 at the left end of thegroove 68 to guide the oil from thegroove 68 toward the outer periphery of theinner spool 59, and a shortconcave groove 70 on the inner periphery of thepiston 66 on the right side spaced slightly apart from theorifice 69. - The above mentioned left
section 66a of the piston has anorifice 75 on theright wall 71 and a shortconcave portion 84 having an inner diameter to allow insertion of aflange 86 between thepush rod 52 and thespool 59 at the left end. - The
spool 59, on the other hand, is provided at the end of thepush rod 52 inserted into theleft chamber 58a through theplug 57 closing the left end of thebody 51, and is placed inside acylindrical chamber 67 within theleft section 66a of the piston. Asspring 72 is provided between the right end of thespool 59 in thechamber 67 and theright wall 71 of theleft section 66a of the piston to impart the force to thespool 59 to constantly push to the left. In the left of thespool 59 is a shortelongated hole 73 along the axial direction of thespool 59 in which apin 74 is fixed to thepiston 66 at both ends of the hole to cross the axis of thespool 59 perpendicularly, Thepin 74 stops thespool 59 from slipping ant of theleft section 66a. - As shown in Figs. 10 and 11, there is provided a
partition wall 76 to divide the inside of thespool 59 intopassages concave groove 79 is cut on the outer periphery of thespool 59 on the left side of thewall 76 and aconcave groove 80 on the outer periphery of thespool 59 on the right side of thewall 76. - Between these
grooves spool 59 is provided anorifice 81 to connect thegroove 70 on the inner periphery of theleft section 66a of the piston and theleft passage 77 inside thespool 59. Anorifice 82 is provided on thegroove 80 on the outer periphery of thespool 59 connecting with thechamber 78 on the right side of thewall 76 in thespool 59. At the left end of theleft passage 77 in thespool 59 is provided anorifice 83 connecting with theleft chamber 58a of the cylinder on the left side of thepiston 59 by passing through aflange 86 between thepush rod 52 and thespool 59. - On the other hand, at the right end of the
piston 66 is provided avalve 85 as shown in Figs. 9, 12 and 13. Thevalve 85 is closed when thepiston 66 and thespool 59 travel to the right in thebody 51 as shown in Figs. 9 and 12, but when thepiston 66 moves to the farthest left inside thebody 51, it contacts saidvertical barrel 65 and opens to release a part of the pressure oil in theright chamber 58b of the cylinder to thetank side passage 61 from thebarrel 65. - In the
travel control device 50 as constructed above, thetravel lever 53 is set at the neutral position as shown in Fig. 9 when the device is to be maintained in the neutral state, and the position is held manually, Thepiston 66 is positioned at the intermediate point of thecylinder 58 at this time, In this state, the pressure oil receiving the mechanical return force of thevibration generator 1 is charged into theright chamber 58b of the cylinder on the right side of thebody 51 through thepassage 90. Thepiston 66 moves to the left by the pressure oil and thespring 62 as shown in Fig. 10, opens the circuit to charge the oil from thepassage 60 on the pump side of thehydraulic pump 55 to the left of thepiston 66, and the pressure increases inside theleft chamber 58a of the cylinder. - The
piston 66 is therefore pushed back to the right as shown in Fig. 11. In the state shown in Fig. 11, the oil from theleft chamber 58a of the cylinder passes through thespool 59 to thetank side passage 61 of thehydraulic pump 55 from thebarrel 65 and lowers the pressure inside theleft chamber 58a on the left of thepiston 66. Thepiston 66 is then pushed again toward the left by the oil charged into theright chamber 58b of the cylinder and the force ofspring 62 as shown in Fig. 10. - When the
travel lever 53 is set at a neutral position and thepush rod 52 in a prescribed position, thepiston 66 repeats the lateral movements discussed above at the intermediate portion of thecylinder 58 to thereby maintain the device in a neutral position. - When the device is to be moved forward from the neutral position, the
travel lever 53 is pushed until the fastest forward position on the left side of the figure is reached or is maintained at an arbitrary angle for setting the speed prior to that position. - In this state, the
spool 59 is pushed to the right by thepush rod 52, or the circuit to charge the oil from the passage of thehydraulic pump 55 to the left side of thepiston 66 opens as shown in Fig. 10, and the pressure inside theleft chamber 58a of the left cylinder of thepiston 66 becomes higher. As a result, thepiston 66 is pushed back to the right as shown in Fig. 11, but since thepush rod 52 is being pushed toward the forward direction (to the right) by thetravel lever 53, thespool 59 is still on the right side while the oil from thepassage 60 continues to flow into theleft chamber 58a of the cylinder, As the oil amount in theleft chamber 58a gradually increases and overcomes the amount of oil flowing into theright chamber 58b of the right cylinder an the right side of thebody 51, thepiston 66 moves to the fastest forward speed position on the extreme right in thecylinder 58 as shown in Fig. 12. - If the
travel lever 53 is stopped at an arbitrary angle for setting the speed before reaching the fastest forward speed position, thepiston 66 repeats the lateral movement as described above at the position with thespool 59 standing still at the end of thepush rod 52. - When the device is brought backward from the neutral position, the
travel lever 53 is pushed to the fastest backward speed position on the left side of the figure as shown in Fig. 13, or is maintained at an arbitrary angle for setting the speed prior to that position. - In this state, the
spool 59 is pulled toward the left by thepush rod 52, or the circuit to charge the oil from theleft chamber 58b of the cylinder at the left of thepiston 66 to thetank side passage 61 of thehydraulic pump 55 opens and the oil charged from thevibration generator 1 through thepassage 90 increases the pressure inside theright chamber 58b of the cylinder on the right side of thepiston 66. As a result, thepiston 66 is pushed back to the left as in Fig. 10, but since thepush rod 52 is being pulled toward the backward direction (to the left) by thetravel lever 53, thespool 59 immediately moves to the left as shown in Fig. 11, and continues charging the oil from theleft chamber 58a of the cylinder on the left side of thepiston 66 to thetank side passage 61 of thehydraulic pump 55. The amount of oil flowing from thevibration generator 1 into theright chamber 58a at the cylinder through thepassage 90 gradually becomes more than that flowing into the cylinder leftchamber 58a from thepump side passage 60, to thereby move thepiston 66 to the position of the fastest backward speed at the extreme left of thecylinder 58 as shown in Fig. 13. - When the
travel lever 53 is stopped at an arbitrary speed setting angle before reaching the position of the fastest backward speed, thepiston 66 repeats the lateral movement as described above with thespool 59 standing stationary at the end of thepush rod 52, to bring the device backward at the prescribed speed. - Differences between constructions of the first embodiment shown in Figs. 1 through 8 and the second embodiment shown in Figs. 9 through 14 are that in the first embodiment the
spool 24 is placed in thebody 21 separate from thepush rod 22 as if being sandwiched by thespring 35 between thepush rod 22 and thespring 32 between thepiston 29, while in the second embodiment thespool 59 is directly attached to the end of thepush rod 52 without a spring between the push rod. - In the construction of the first embodiment, when the
piston 29 is pushed to the left from the neutral position shown in Fig. 5 via thepassage 45 by the oil charged from thevibration generator 1, thepush rod 22 is separated from thespool 24 and supported by thespring 27 in thebody 21 at a predetermined position, and the device is maintained in a neutral position even when the operator takes his/her hand off thetravel lever 23. In the construction of the second embodiment, however, when thepiston 66 is pushed to the left by the oil sent from thevibration generator 1 via thepassage 90, the operator must hold thetravel lever 53 by hand in order to prevent thepush rod 52 from also moving to the left. The two embodiments are the same in respect of the rest of the basic construction. - As described above, the travel control device for the vibrating plate compactor according to the present invention is provided with a piston to receive the mechanical return force from the vibration generator in the cylindrical body on one hand, and a servo valve spool which can supply the pressure from the hydraulic pump to resist the mechanical return force acting on the piston by manipulating the push rod on the other, so that the device can supply the pressure to one side of the piston from the hydraulic pump to resist the powerful mechanical return force from the vibration generator even when the compactor is very large with its weight exceeding 500 kg, and the switching operation of the travel lever may be made lighter, It is also possible to control the speed at any position in the forward or backward directions with the travel lever in operation.
- The construction of the first embodiment, in particular, provides a spool between the piston and the push rod via a spring in order to enable transmission of the force to operate the push rod to the spool via a spring and to further make the switching operation of the travel lever lighter. When the operator lifts his/her hand off the operating lever with the device in a neutral condition, the travel lever maintains its neutral condition automatically, thus enhancing safety by eliminating any risks of the device running out of control.
Claims (10)
- A travel control device (20, 50) for a vibrating plate compactor provided with an eccentric rotor (6) on one of two parallel axes connected to each other of which rotor (5) being able to vary the rotational phase of the eccentric rotor (6) on the other axis, a piston rod (12) inserted slidably into the shaft (4) to support the eccentric rotor (6), and a vibration generator (1) having a hydraulic cylinder (18) at one of the axes to switch the rotation of said eccentric rotor (6) in the forward and backward directions by moving the piston rod (12) axially by a force imparted from outside to resist the mechanical return force generated by rotation of said eccentric rotor, the travel control device (20, 50) imparting the outside force to resist said mechanical return force to the hydraulic cylinder (18) of said vibration generator (1)
characterized by a piston (29, 66) in a cylindrical body (21, 51) to receive the mechanical return force from said vibration generator (1) at one end and pressure oil from an outside hydraulic pump (41, 55) at the other end, a push rod (22, 52) for switching the travel direction inserted into the body (21, 51) at one end, and a spool (24, 59) for servo valve to supply the pressure oil from said hydraulic pump (41, 55) to the side of the piston (29, 66) opposite the side receiving said mechanical return force . - The travel control device as claimed in claim 1,
wherein said spool (24) is positioned at the center (21b) of the body (21), both ends of said spool (24) being supported by springs (32, 35) between the push rod provided at one end of the body (21) and the piston (29) at the other end of the body (21),a passage (45) on the vibration generator side being provided to supply mechanical return force from said vibration generator (1) to the space between the spool (24) and the piston (29),and a passage (42) on the pump side being provided to supply the pressure oil from a hydraulic pump (41) opposing the mechanical return force between said spool (24) and the outside of the piston (29). - The travel control device as claimed in claim 1 or 2,
wherein the inside of one end of the body (21) through which one end of the push rod (22) is inserted is shaped like a cylinder (26),and the device is provided with a spring bearing (25) slidably inserted over the other periphery of one end of said push rod (22) and the spring (27) to support said push rod (22) in a neutral position over the outer periphery of the spring bearing (25). - The travel control device as claimed by one of claims 1 to 3,
wherein said spool (24) to be positioned in the center chamber (21b) of the body (21) has flanges (34a, 34b) on both ends, the length of a hole (33) through which said spool (24) is inserted in the center chamber (21b) is set shorter than the interval of the flanges (34a, 34b) on both ends of said spool (24), and the device is provided with a concave groove (38) of the length to allow insertion of one end of a piston rod (30) extending toward said spool (24) from said piston (29) at one end of said hole (33) on the side adjacent to said piston (29). - The travel control device as claimed in one of claims 1 to 4,provided with a passage supplying the pressure oil from the hydraulic pump (41) through a concave groove (39), cut on the outer periphery of said spool (24), from the pump side passage (42) into the cylinder (28) outside the piston (29) in the spool (24) at the center (21b) of the body (21) by laterally moving the spool (24) by manipulating the push rod (22) and a tank side passage (44) to discharge the pressure oil inside the outside cylinder (28) of said piston (29) from said pressure oil passage to a tank via another concave groove (40) cut on the outer periphery of the spool (24).
- The travel control device as claimed in one of claims 1 to 4,
wherein one end of the push rod (22) is formed like a cylinder (26), and a spring (35) is positioned between the end of the cylinder and one end of the spool (24) positioned at the center (21b) of the body (21). - The travel control device as claimed in one of claims 1 to 6,
wherein one end of the piston rod (30) extending toward said spool (24) of the center chamber (21b) from said piston (29) positioned at one end of the body (21) is shaped like a cylinder (30a), and a spring (32) is positioned between the end of the cylinder (30a) and one end of said spool (24) positioned in the center (21b) of the body (21). - The travel control device for vibrating plate compactor as claimed in claim 1,
wherein the piston (66) is positioned in a cylindrical body (51) having a passage (61) on the vibration generator side to receive the mechanical return force from said vibration generator (1) at one end, and a push rod (52) integrally provided with a spool (59) at one end is inserted into the other end of said body (51), with said spool (59) being inserted into one end of said piston (66) and a pump side passage (60) between said piston (66) and said spool (59) to supply the pressure oil resisting said mechanical return force from a hydraulic pump (55) outside the body (51) to the cylinder (58) on the push rod side of the piston (66) through said spool (59). - The travel control device as claimed in claim 1 or 8,
wherein said piston (66) can reciprocally travel for the length of an elongated hole bore (63) at the center of said piston (66) through which a vertical barrel (65) is inserted in the direction perpendicular to the axial direction of said piston (66), and a tank side passage (61) is provided at one end of the barrel (65) to release the pressure oil resisting said mechanical return force inside the cylinder (58) on the push rod side of the piston (66) through the spool (59), between the piston (66) and the spool (59), and through the piston (66) to the tank. - The travel control device as claimed in one of claims 1, 8 or 9,
wherein the spool (59) has an elongated hole (73) at one end thereof through which is inserted a pin (74) in the direction perpendicular to the axial direction of said spool (59) so that said spool (59) can reciprocally travel inside the piston (66) for the length of the elongated hole (73) in order to switch the pressure oil supplied from the pump side passage (60) to the cylinder (58) on the push rod side.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP14666398 | 1998-05-13 | ||
JP14666398A JP3318528B2 (en) | 1998-05-13 | 1998-05-13 | Forward and backward operation mechanism of vibration compaction machine |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0960659A1 true EP0960659A1 (en) | 1999-12-01 |
EP0960659B1 EP0960659B1 (en) | 2000-08-23 |
Family
ID=15412816
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP19990108350 Expired - Lifetime EP0960659B1 (en) | 1998-05-13 | 1999-04-28 | Travel control device for vibrating plate compactor |
Country Status (4)
Country | Link |
---|---|
EP (1) | EP0960659B1 (en) |
JP (1) | JP3318528B2 (en) |
DE (1) | DE69900009T2 (en) |
ES (1) | ES2151766T3 (en) |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2002087789A1 (en) | 2001-05-02 | 2002-11-07 | Wacker Construction Equipment Ag | Controller for an unbalanced mass adjusting unit of a soil compacting device |
US6981558B2 (en) | 2001-05-02 | 2006-01-03 | Wacker Construction Equipment Ag | Controller for an unbalanced mass adjusting unit of a soil compacting device |
EP2789862A1 (en) * | 2013-04-10 | 2014-10-15 | ABI Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH | Oscillation excite for construction machines |
US9289799B2 (en) | 2013-04-10 | 2016-03-22 | Abi Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik Und Vertriebsgesellschaft Mbh | Vibration exciter for construction machines |
CN108005056A (en) * | 2017-12-06 | 2018-05-08 | 郑州诚合信息技术有限公司 | A kind of depositing dust formula rammer easy to remove |
Families Citing this family (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4510321B2 (en) * | 2001-04-19 | 2010-07-21 | 三笠産業株式会社 | Vibration compaction machine forward / reverse switching hand pump |
EP1568420B1 (en) * | 2004-02-29 | 2018-08-15 | BOMAG GmbH | Device and method for controlling a vibrating machine |
DE102004015589A1 (en) * | 2004-02-29 | 2005-09-15 | Bomag Gmbh | Controller for unbalance adjustment of vibrating soil-compactor, controls valve according to pulse-width modulation signal to set relative position of unbalance weights |
DE102012025378A1 (en) | 2012-12-27 | 2014-07-03 | Wacker Neuson Produktion GmbH & Co. KG | VIBRATOR FOR FLOOR COMPACTERS |
CN110124975A (en) * | 2019-05-30 | 2019-08-16 | 湖北普爱药业有限公司 | A kind of material packet leveling device |
JP6987423B1 (en) * | 2021-05-26 | 2022-01-05 | 三笠産業株式会社 | Breather for vibration device |
Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4356736A (en) * | 1979-03-09 | 1982-11-02 | Wacker-Werke Gmbh & Co. Kg | Imbalance-oscillation exciter |
US4771645A (en) * | 1986-06-27 | 1988-09-20 | Dynapac Ab | Vibrating plate compactor |
-
1998
- 1998-05-13 JP JP14666398A patent/JP3318528B2/en not_active Expired - Fee Related
-
1999
- 1999-04-28 EP EP19990108350 patent/EP0960659B1/en not_active Expired - Lifetime
- 1999-04-28 ES ES99108350T patent/ES2151766T3/en not_active Expired - Lifetime
- 1999-04-28 DE DE1999600009 patent/DE69900009T2/en not_active Expired - Fee Related
Patent Citations (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US4356736A (en) * | 1979-03-09 | 1982-11-02 | Wacker-Werke Gmbh & Co. Kg | Imbalance-oscillation exciter |
US4771645A (en) * | 1986-06-27 | 1988-09-20 | Dynapac Ab | Vibrating plate compactor |
Cited By (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2002087789A1 (en) | 2001-05-02 | 2002-11-07 | Wacker Construction Equipment Ag | Controller for an unbalanced mass adjusting unit of a soil compacting device |
US6981558B2 (en) | 2001-05-02 | 2006-01-03 | Wacker Construction Equipment Ag | Controller for an unbalanced mass adjusting unit of a soil compacting device |
EP2789862A1 (en) * | 2013-04-10 | 2014-10-15 | ABI Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik und Vertriebsgesellschaft mbH | Oscillation excite for construction machines |
US9289799B2 (en) | 2013-04-10 | 2016-03-22 | Abi Anlagentechnik-Baumaschinen-Industriebedarf Maschinenfabrik Und Vertriebsgesellschaft Mbh | Vibration exciter for construction machines |
CN108005056A (en) * | 2017-12-06 | 2018-05-08 | 郑州诚合信息技术有限公司 | A kind of depositing dust formula rammer easy to remove |
Also Published As
Publication number | Publication date |
---|---|
DE69900009T2 (en) | 2001-04-05 |
JP3318528B2 (en) | 2002-08-26 |
EP0960659B1 (en) | 2000-08-23 |
DE69900009D1 (en) | 2000-09-28 |
ES2151766T3 (en) | 2001-01-01 |
JPH11323817A (en) | 1999-11-26 |
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