CN1445415A - Compacting roller - Google Patents
Compacting roller Download PDFInfo
- Publication number
- CN1445415A CN1445415A CN03110525A CN03110525A CN1445415A CN 1445415 A CN1445415 A CN 1445415A CN 03110525 A CN03110525 A CN 03110525A CN 03110525 A CN03110525 A CN 03110525A CN 1445415 A CN1445415 A CN 1445415A
- Authority
- CN
- China
- Prior art keywords
- piston
- cylinder
- unbalance
- compression roll
- rolling element
- 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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- E—FIXED CONSTRUCTIONS
- E01—CONSTRUCTION OF ROADS, RAILWAYS, OR BRIDGES
- E01C—CONSTRUCTION OF, OR SURFACES FOR, ROADS, SPORTS GROUNDS, OR THE LIKE; MACHINES OR AUXILIARY TOOLS FOR CONSTRUCTION OR REPAIR
- E01C19/00—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving
- E01C19/22—Machines, tools or auxiliary devices for preparing or distributing paving materials, for working the placed materials, or for forming, consolidating, or finishing the paving for consolidating or finishing laid-down unset materials
- E01C19/23—Rollers therefor; Such rollers usable also for compacting soil
- E01C19/28—Vibrated rollers or rollers subjected to impacts, e.g. hammering blows
- E01C19/286—Vibration or impact-imparting means; Arrangement, mounting or adjustment thereof; Construction or mounting of the rolling elements, transmission or drive thereto, e.g. to vibrator mounted inside the roll
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- Engineering & Computer Science (AREA)
- Architecture (AREA)
- Civil Engineering (AREA)
- Structural Engineering (AREA)
- Road Paving Machines (AREA)
- Rolls And Other Rotary Bodies (AREA)
- Apparatuses For Generation Of Mechanical Vibrations (AREA)
Abstract
The invention relates to a compaction roller having at least one rolling body with a vibratory drive which comprises a drivable exciter shaft with an unbalance. The shaft is mounted axially with respect to the rolling body and in the body. The unbalance, which comprises an unbalance cylinder arranged centrally with respect to the axis of the rolling body, is held by the exciter shaft and has an unbalance piston which can be adjusted hydraulically radially with respect to the axis of the rolling body by means of an adjusting device.
Description
Technical field
The present invention relates to a kind of as claim 1 compression roll as described in the preamble.
Background technology
In the ground works or the construction of building the road, wish as quickly as possible with uncombined, waterpower in conjunction with or the bituminous bond material be compacted to the Pu Shi (Proctor) or Marshall (Marshall) density of regulation, but to prevent overcompaction simultaneously, especially under the wearing layer situation, reduce the particle fragmentation of mineral constituent.
On bitumeniferous road surface, bond well in order to ensure interlayer, or under the wearing layer situation, guarantee the height chucking power, in compacting process, should avoid smooth surface.Under the situation of bituminous material, because the cooling of material reduces compactibility, and can not reach the final densities of regulation in worst situation, therefore for number of machine passes is few, the optimizer system parameter is set in absolute demand.When compacting drainage asphalt (drain asphalt) (perforate pitch), can not seal near the hole in the zone on surface, so that the draining that acquisition is wanted, and when rolling in the contact zone of automobile between tire and road surface, can reduce the effect of so-called " air pump (air-pumping) ".
In the excessive place of the Oscillation Amplitude of rolling element, or vibration frequency is near the place as the natural frequency of bridge construction or other structure, those places may be damaged, therefore in these cases, especially relate under the situation of compression roll with the eccentric loading of tradition turning cylinder, must close vibration, to avoid damage.As a result, then in order to reach the final densities of regulation,, need repeatedly the static compaction roller to pass through if reach final density by static compaction roller (static roller) fully.
The known vibration compaction roller that is used for the non-binding soil of compacting and waterpower or bituminous layer disposes the eccentric turning cylinder that loads.In this case, provide fixing unbalance at least one.As common situation, also may additionally provide conversion weight (changeover weight), so that produce two different nominal amplitude.But, can not between two nominal amplitudes, regulate amplitude.
Known equally, 0053598B is similar with European patent EP, and asphalt compaction can utilize rolling element by being known as vibration, rather than annular or directionality are vibrated and carried out.But, owing to only come compacting, and alternately bear shear stress, and compacting can not take place to the certain depth by the linear load of a static state at this material.Compulsory slip between rolling element and ground causes traction problems inevitably.Vibration moment is produced by two unbalance axles, and these two axles are parallel to the turning cylinder of roller to be installed, and 180 ° of their unbalance deflections, along same direction synchronous operation.Under bitumeniferous material situation, oscillation effect can cause undesired ripple, smooth effect and dead-end pore.
In compression roll, be well known that equally at unbalancing machine that can rotate around the rolling axon and the fixing joint of the adjustable angle between the unbalancing machine, so that formed unbalance can the setting in the mode of electrodeless variation.
German document DE69425111 T2 discloses a kind of compression roll, and it is unbalance can regulate in the mode of electrodeless variation by hydraulic cylinder and connecting rod, but this unbalancing machine is arranged to respect to rolling axon lateral rotation.But this is very expensive and complicated.
In the compression roll of in German patent application DE4129182A1 and European patent application EP 0954187A2, describing, the directionality vibrator comprises at least two driver axles, they move in opposite directions, and the power of its generation can forward vertical direction to from horizontal direction in the mode of electrodeless variation, and need not moment.Nominal amplitude or unbalance not change in this system.Especially relating under the situation of horizontal vibration, this also is the situation that undesired ripple, smooth effect and closed pore can take place.
German patent application DE10031617A1 also discloses a kind of vibration machine that is used for compactor, wherein a driver axle is provided with a unbalancing machine, relative this driver diameter of axle to the cylinder of arranging and having a spring-loaded piston, and this piston is used to make unbalance self-regulating purpose by the centrifugal force that changes by the change rotating speed.Except that the height of centrifugal force with variable eccentricity and rotating speed non-linear can not the full remuneration metal or this fact of elastic force of hydraulic spring grease cup, accurately be furnished with an amplitude in this each frequency equally.In addition, from halted state, starting this unbalance axle can only be with highly unbalance acceleration.
Summary of the invention
The purpose of this invention is to provide a kind ofly as claim 1 compression roll as described in the preamble, it is to specific road construction material or local environment, and the existence such as bridge and sensitive structure of vibration and building has best vibration adaptation.
This goal of the invention can realize by the content of claim 1 characteristic.
Hold and open above, be provided with a power cylinder, its chamber is connected with this unbalanced cylinder, and be connected to a hydraulic power source through a controlled valve, to be used for the purpose of supply leakage of oil, center or the centre position of this valve between the end positions of unbalance piston closed, thus, can increase or reduce nominal amplitude.
This makes and to carry out the leakage of oil supply and demarcation becomes possibility that the result can not weaken consolidation effect by doing like this.And, the nominal amplitude that can regulate the rolling element vibration in mode simple in structure.This further makes the vibration frequency of vibrating roller and the speed of service can adapt to nominal amplitude automatically, and then obtains best compacting result again.Therefore, can guarantee thick-layer (as anti-fog layer), the compacting of the thin layer surface course of compacting pitch (as be used for) and sensitive layer (as perforate pitch).
Other purpose of the present invention, advantage and embodiments of the invention can obtain by following explanation and claim.
Description of drawings
The present invention will be described in more detail for one exemplary embodiment with reference to the accompanying drawings.
Fig. 1 is the diagrammatic side view of tandem roller;
Fig. 2 is the sectional view of rolling element of the tandem roller of Fig. 1;
Fig. 3 is the detailed drawing of Fig. 2;
Fig. 4 a and 4b are two embodiment of nominal amplitude that are used to regulate the tandem roller of Fig. 1;
Fig. 5 a to 5c is three the different work settings of embodiment that are used for the tandem roller of Fig. 1;
Fig. 6 a to 6c is three the different work settings of another embodiment that are used for the tandem roller of Fig. 1.
The specific embodiment
Tandem roller shown in Figure 1 comprises the superstructure 1, the rolling element 2 and 3 that have driver's cabin, and their are installed in forward and backward place under the described superstructure 1 through rotating coupling 4 with turning to.Between two rolling elements 2,3, be an engine room 5, the driving motor be housed, normally diesel engine in it.
As shown in Figure 2, before or after rolling element 2,3 comprise the corresponding tire end plate 7 that radially extends of two (tyre halves) 6a, 6b of the tire that is arranged side by side vertically half and, this tire end plate 7 has a center through hole.Corresponding bearing flange 8 is fastened on the tire end plate 7.Through two bearing flanges 8 and spacer tube 9, by 10, two tires of bearing, half 6a of, 6b is connected to each other so that can be around the rotational of rolling element, wherein this bearing 10 for example is the roller bearing that is arranged between bearing flange 8 and the spacer tube 9.
Can be connected to rotation coupling 4 on the superstructure 1 flexibly is connected to corresponding hollow hydraulic pressure in both sides through damping piece 11 (for example rubber metal parts) and flange plate 11a and moves on the motor 12 with turning to.At outlet side, mobile motor 12 is connected in adjacent bearing flange 8 through flange 13, and drives corresponding tire half 6a of, 6b. thus
What be in rolling element central authorities is driver axle 14, and it is driven by hydraulic vibration motor 15, and installs with respect to bearing flange 8 through bearing.Unbalanced cylinder 16 medially is installed in 14 internal drillings of driver axle.For this purpose, unbalanced cylinder 16 has a corresponding axle collar, and at its opposite side, has thread segment, to be used for by retaining ring and the clamping of a pair of nut.Unbalanced cylinder 16 holds unbalance piston 17, so that it can be regulated with respect to rolling axon hydraulic radial.
When changing eccentricity, be enough in driver axle 14 to realize that the unbalance of nominal amplitude of the minimum of rolling element can add in the mode of electrodeless variation by the unbalance piston of translation 17.For the adjustable range of acquisition nominal amplitude in the structure space of minimum is big as far as possible, unbalance piston 17 can be filled with lead.
For space in the lubricated spacer tube 9 and adjacent bearing etc., in one of bearing flange 8, have oil-feed and go out oil burner nozzle 20.
As shown in Figure 3, unbalance piston 17 pressurizations are to be undertaken by the oil mass of the accurate measurement that is used for mobile unbalance piston 17 by rotation axle bush 21, and rotation axle bush 21 is suspended from one of mobile motor 12 with low vibration by rubber spring 22 and additional vibration object 22.Vibration object 23 holds the adapter 24 of supporting piston 25, so that piston can move.This piston links to each other with another piston 27 that driver axle 14 holds through managing 26.Since thermal expansion, radial and axial seal 28 compensation that move through piston 25,27 between rotation axle bush 21 and the driver axle 14.Pin 29 prevents rotational slide between the adapter 24 of seal 28 and driver axle 14 or rotation axle bush 21.
In the embodiment among Fig. 4 a, be used to change the regulating piston 34 of the required oil mass in the position of unbalance piston 17 by mobile power cylinder 34a and measure.At this, the piston rod 30 of regulating piston 34 is connected on the trapezoidal or spherical screw drive 31, and this screw driven axle is not removable (self-locking) under tensile stress or action of compressive stress.This screw drive 31 is driven by electric power or hydraulic motor 32.To the measurement of the mobile increment of piston rod, or as suitable words the angular measurement of screw drive 31 (being one at this preferably, therefore not shown) is used for setting the eccentricity or the nominal amplitude of unbalance piston 17.In order to demarcate and for the purpose of leakage of oil compensation, to be provided with one second oil in piston side and to connect, its 2/2 can automatically be changed flow locations to valve 33 as the function of mode of operation.
According to the embodiment shown in Fig. 4 b, the required oil mass in position that adopts regulating piston 34 and piston rod 30 thereof to change unbalance piston 17 is revised into variable oil mass at piston rod side.For this purpose, an electromagnetism 3/3 to the valve actuating that circulates as follows, that is, make regulating piston 34 can move very little distance.When 3/3 when valve 35 is connected on the pressure, regulating piston 34 moves along the piston side direction, in the time of on being connected to fuel tank, because the centrifugal force of unbalance piston 17 and moving along the piston rod side direction.At this, 3/3 replaces the self-locking action of the screw drive 31 of Fig. 4 a to the locking O position of valve 35.At this, be the centrifugal degree of setting unbalance piston 17 or the purpose of nominal amplitude, the proprietary function that has the regulating piston 34 of piston rod 30 is the measurement to mobile increment.Those of eccentricity and leakage of oil compensation and Fig. 4 a are corresponding.
Fig. 5 a to 5c has described in conjunction with all places of the unbalance piston 17 of the adjusting device of Fig. 4 a (being applicable to the adjusting device of Fig. 4 b too).In following four duty processes, unbalance piston 17 is in the position shown in Fig. 5 a.
1. when vibrating device stopped to move with diesel engine, the oil pressure of unbalance piston 17 was corresponding to the pressure of valve 33 entrance with 2/2, and this this connection of valve base is with in this mode of operation current downflow.As a result, the leakage of oil amount is by supply, simultaneously unbalance piston 17 overcome " minimum unbalance degree " stop (demarcation) along minimum centrifugal degree by the application of force.
2. vibratory driver should quicken as quickly as possible with the moment of inertia of minimum, till the operating frequency that reaches minimum.As a result, with minimum nominal amplitude rapidly by resonance range, thereby coupling assembling only stands stress slightly as rotating joint 4 or superstructure 1 and connector thereof.When reaching minimum frequency of operation, this 2/2 flowing to valve 33 obstruction oil.Leakage of oil supply and demarcation finish simultaneously automatically.
3. minimum nominal amplitude is set at maximum vibration frequency place.Open 2/2 to valve 33, leakage of oil is as a result gone forward side by side rower calmly by supply.
4. when closing vibratory driver, for little moment of inertia brake vibration driver, unbalance piston 17 moves along the directions of minimum nominal amplitude automatically.In case the position of regulating piston 34 consistent with shown in Fig. 5 a, 2/2 inlet pressure to valve 33 flows with regard to being connected.From this constantly, leakage of oil is able to supply and system is demarcated.
When unbalance piston 17 was in position shown in Fig. 5 c, 2/2 closed to valve, and can not supply leakage of oil and demarcation.Nominal amplitude increases or reduces from this mode of operation in the mode of electrodeless variation.Operating frequency can be along the direction servo-actuated control of less nominal amplitude, as the situation of unbalance piston 17 along the position of big nominal amplitude.
When rotating driver was closed, unbalance piston 17 moved along minimum nominal amplitude direction from the position shown in Fig. 5 b and the 5c immediately, and this is irrelevant with the increase operating frequency.
In order to realize the compacting of best soil or pitch, as mentioned above, vibration frequency coupling nominal amplitude.As the function of vibration frequency, simultaneously can the best rolling speed of automatic setting, and be shown to this roller man for this reason.As the function of ground surface density (hardness), not only can manual adjustments but also can control automatically in the position of unbalance piston 17.In the tandem roller vibrating roller, can be only at the preceding or equipped unbalance device that can regulate in the above described manner in the back or on two rolling elements 2,3 only.
In the embodiment shown in Fig. 6 a to 6c, be provided with the hydraulic motor 32 that a direction valve 35 replaces Fig. 5 a to 5c, this valve is connected on the chamber of the power cylinder 34 on the piston rod side, and direction valve 33, at this is a three-way valve, is connected on power cylinder 34 chambers of regulating piston 34 upstreams.
In the embodiment shown in Fig. 6 a, after regulating piston 34 was withdrawn fully, vibrator cut out, and unbalanced cylinder 16 is oil-filled through pump 37 from hydraulic power source.For this reason, when vibrator cut out, direction valve 33 was connected shown in Fig. 6 a.Pressure limiting valve 36 is connected to from pump 37 to direction valve on 33 the pipeline.If described valve 36 responses this means that unbalanced cylinder 16 is full of oil fully.
With reference to Fig. 6 b, when reaching the complete oil-overflow state of unbalanced cylinder 16, direction valve 33 commutations, thereby oil can flow back to hydraulic power source from power cylinder 34a, especially the upstream chamber from regulating piston 34 flows back to through pressure limiting valve 38, and the previous direction valve of cutting out 35 opens, so that hydraulic oil can be regulated regulating piston 34.Then, regulate the interior oil of cylinder 34a and turn back to hydraulic power source fully, thus, system demarcates simultaneously.
With reference to Fig. 6 c, if reach this state, direction valve 33,35 cuts out, and vibrator is opened.If reach a CF then, as 28Hz, by the corresponding aperture of direction valve 35, amplitude is from the position adjustments of the minimum radius shown in Fig. 6 c.
In this embodiment, except that the leakage of oil supply and demarcating, the total amount that hydraulic oil also takes place in system each vibratory compaction stop or the occasion of interrupting in the additional exchange of vast scale at least also takes place, this system comprises cylinder 16 and 34a.Ageing for hydraulic oil is favourable with cooling off this.
The one exemplary embodiment with explanation that is clearly exemplified for those skilled in the art is not to be intended to limit the present invention, but under the scope that does not break away from the spirit of the present invention defined in the claim, can make multiple change and modification.
Claims (12)
1. compression roll, rolling element (2 with at least one band vibratory driver, 3), this vibratory driver comprises the driven driver axle (14) with certain unbalancing machine, described axle is this rolling element (2 relatively, 3) axially be installed in the described rolling element, this unbalancing machine comprises relative rolling element (2,3) the axis unbalanced cylinder of arranging (16) placed in the middle, and this unbalanced cylinder is supported by driver axle (14), and has a unbalance piston (17), this piston (17) is rolling element (2 relatively, 3) axis hydraulic radial is regulated, and hydraulic fluid can be supplied with this unbalanced cylinder (16) by the boring (18) of an outside adjusting device in driver axle (14), make the electrodeless variation of nominal amplitude ground adapt to the environment of paving the way simultaneously, this adjusting device has power cylinder (34a), the chamber that this power cylinder has power piston (34) and is connected with unbalanced cylinder, it is characterized in that, purpose for the leakage of oil supply, the chamber that power cylinder (34a) is connected with unbalanced cylinder (16) is connected to hydraulic power source through controlled valve (33), this valve cuts out when being in the center at unbalance piston (17), increases or reduce nominal amplitude thus.
2. compression roll according to claim 1 is characterized in that, when reaching minimum frequency of operation, valve (33) cuts out.
3. compression roll according to claim 1 and 2 is characterized in that, after vibratory driver is closed, can carry out the hydraulic oil exchange between unbalanced cylinder (16) and hydraulic oil source via controlled valve (33).
4. compression roll according to claim 3 is characterized in that, after vibratory driver is closed, can carry out the hydraulic oil exchange through this controllable valve (33) between power cylinder (34a) and hydraulic oil source.
5. according to claim 3 or 4 described compression rolls, it is characterized in that along with power piston (34) retraction, controllable valve (33) can be connected on the hydraulic oil source.
6. compression roll according to claim 5 is characterized in that, oil-filled along with power piston (34) retraction and unbalanced cylinder (16), controlled valve (33) can be connected with hydraulic oil source, and power piston (24) is extensible.
7. according to each described compression roll in the claim 1 to 6, it is characterized in that unbalanced cylinder (16) is connected on the adjusting device through rotation axle bush (21), this axle bush is supported on the rolling element (2,3) through damping piece (22).
8. compression roll according to claim 7 is characterized in that, is furnished with pipeline (26) between rotation axle bush (21) and driver axle (14), and this pipeline has the connection of end play ground in the mode of rotational fixation and by the piston (25,27) in its end.
9. according to each described compression roll in the claim 1 to 8, it is characterized in that power piston (34) can machinery or adjusting hydraulically.
10. compression roll according to claim 9 is characterized in that, the position of power piston (34) can be by detection arrangement monitors.
11., it is characterized in that adjusting device is as the function of the measured value of the compaction capacity of rolling element (2,3) and controlled according to claim 9 or 10 described compression rolls.
12., it is characterized in that unbalance piston is filled with heavy metal in (17) according to each described compression roll in the claim 1 to 11.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10210049A DE10210049B4 (en) | 2002-03-07 | 2002-03-07 | compaction roller |
| DE10210049.7 | 2002-03-07 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1445415A true CN1445415A (en) | 2003-10-01 |
| CN100529263C CN100529263C (en) | 2009-08-19 |
Family
ID=27740680
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB031105254A Expired - Fee Related CN100529263C (en) | 2002-03-07 | 2003-03-07 | Compacting roller |
Country Status (5)
| Country | Link |
|---|---|
| US (1) | US20030223817A1 (en) |
| EP (1) | EP1342849B1 (en) |
| JP (1) | JP4203725B2 (en) |
| CN (1) | CN100529263C (en) |
| DE (2) | DE10210049B4 (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105268621A (en) * | 2015-11-11 | 2016-01-27 | 王存伟 | Stepless amplitude-variable vibrator |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102006030628B4 (en) * | 2006-07-03 | 2021-03-04 | F. Weyhausen Ag & Co. Kg Maschinenfabrik | Device for compacting a subsoil |
| US20110158745A1 (en) * | 2009-12-31 | 2011-06-30 | Caterpillar Paving Products Inc. | Vibratory system for a compactor |
| DE102021200285A1 (en) | 2021-01-14 | 2022-07-14 | Robert Bosch Gesellschaft mit beschränkter Haftung | Compaction vehicle in which a travel drive and a vibration unit are supplied with pressurized fluid from a common supply point |
| CN113846540B (en) * | 2021-10-22 | 2024-02-09 | 李亚辉 | Road bridge engineering road surface prosthetic devices |
| CN115157717B (en) * | 2022-06-29 | 2024-02-09 | 中化工程沧州冷却技术有限公司 | Production process of glass fiber reinforced plastic pipeline for cooling tower |
| CN115369720B (en) * | 2022-07-29 | 2024-08-16 | 许慧保 | Electrodeless variable-frequency directional hydraulic vibratory roller |
Family Cites Families (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3059483A (en) * | 1960-05-31 | 1962-10-23 | Continental Oil Co | Vibrator with hydraulically controlled eccentricity |
| US3656419A (en) * | 1969-04-01 | 1972-04-18 | American Hoist & Derrick Co | Vibratory roller |
| US4105356A (en) * | 1977-05-19 | 1978-08-08 | Koehring Corporation | Vibratory roller |
| SE426719B (en) * | 1980-12-03 | 1983-02-07 | Thurner Geodynamik Ab | PROCEDURE AND DEVICE FOR PACKING A MATERIAL LAYER |
| AU570233B2 (en) * | 1983-02-18 | 1988-03-10 | Bowater Tutt Industries Pty. Ltd. | Vibratory mechanism |
| US4759659A (en) * | 1987-07-01 | 1988-07-26 | Fernand Copie | Variable vibrator system |
| DE4129182A1 (en) * | 1991-09-03 | 1993-03-04 | Bomag Gmbh | COMPRESSOR |
| AU692479B2 (en) * | 1993-11-30 | 1998-06-11 | Sakai Heavy Industries, Ltd. | Vibrating mechanism and apparatus for generating vibrations for a vibration compacting roller with a variable amplitude |
| FI107365B (en) * | 1998-04-27 | 2001-07-13 | Nokia Mobile Phones Ltd | A method and system for detecting variable data processing in a communication link |
| US6460006B1 (en) * | 1998-12-23 | 2002-10-01 | Caterpillar Inc | System for predicting compaction performance |
| IT1307472B1 (en) * | 1999-07-13 | 2001-11-06 | Bitelli Spa | VIBRATING DRUM PERFECTED FOR SOIL COMPACTING MACHINES. |
| JP3725769B2 (en) * | 1999-10-28 | 2005-12-14 | 酒井重工業株式会社 | Hand guide roller |
| DE10031617A1 (en) * | 2000-06-29 | 2002-01-17 | Wacker Werke Kg | Vibration exciter with amplitude adjustment |
-
2002
- 2002-03-07 DE DE10210049A patent/DE10210049B4/en not_active Expired - Fee Related
-
2003
- 2003-02-22 EP EP03003966A patent/EP1342849B1/en not_active Expired - Lifetime
- 2003-02-22 DE DE50310053T patent/DE50310053D1/en not_active Expired - Lifetime
- 2003-03-05 JP JP2003059232A patent/JP4203725B2/en not_active Expired - Fee Related
- 2003-03-06 US US10/382,440 patent/US20030223817A1/en not_active Abandoned
- 2003-03-07 CN CNB031105254A patent/CN100529263C/en not_active Expired - Fee Related
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105268621A (en) * | 2015-11-11 | 2016-01-27 | 王存伟 | Stepless amplitude-variable vibrator |
| CN105268621B (en) * | 2015-11-11 | 2018-06-05 | 王存伟 | Stepless luffing vibrator |
Also Published As
| Publication number | Publication date |
|---|---|
| EP1342849A2 (en) | 2003-09-10 |
| EP1342849A3 (en) | 2004-12-01 |
| JP4203725B2 (en) | 2009-01-07 |
| US20030223817A1 (en) | 2003-12-04 |
| JP2004003296A (en) | 2004-01-08 |
| DE50310053D1 (en) | 2008-08-14 |
| CN100529263C (en) | 2009-08-19 |
| DE10210049B4 (en) | 2004-03-25 |
| EP1342849B1 (en) | 2008-07-02 |
| DE10210049A1 (en) | 2003-10-09 |
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| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20090819 Termination date: 20170307 |