CN110588270A - Vibration reduction mechanism of stacking machine - Google Patents
Vibration reduction mechanism of stacking machine Download PDFInfo
- Publication number
- CN110588270A CN110588270A CN201910679901.0A CN201910679901A CN110588270A CN 110588270 A CN110588270 A CN 110588270A CN 201910679901 A CN201910679901 A CN 201910679901A CN 110588270 A CN110588270 A CN 110588270A
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- CN
- China
- Prior art keywords
- cross beam
- damping
- oil cylinder
- axle
- oil
- 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.)
- Withdrawn
Links
- 238000013016 damping Methods 0.000 claims abstract description 57
- 239000003921 oil Substances 0.000 claims description 96
- 230000035939 shock Effects 0.000 claims description 52
- 238000010521 absorption reaction Methods 0.000 claims description 34
- 239000010720 hydraulic oil Substances 0.000 claims description 9
- 238000004146 energy storage Methods 0.000 claims description 7
- 239000010985 leather Substances 0.000 claims description 6
- 238000000034 method Methods 0.000 claims description 2
- 238000003825 pressing Methods 0.000 description 12
- IJGRMHOSHXDMSA-UHFFFAOYSA-N Atomic nitrogen Chemical compound N#N IJGRMHOSHXDMSA-UHFFFAOYSA-N 0.000 description 6
- 238000012360 testing method Methods 0.000 description 6
- 239000006096 absorbing agent Substances 0.000 description 5
- 230000002035 prolonged effect Effects 0.000 description 5
- 238000003466 welding Methods 0.000 description 4
- 239000007789 gas Substances 0.000 description 3
- 229910052757 nitrogen Inorganic materials 0.000 description 3
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical compound [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 239000013589 supplement Substances 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 229910052742 iron Inorganic materials 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 238000011084 recovery Methods 0.000 description 1
- 230000003014 reinforcing effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
- B60G13/02—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally
- B60G13/04—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally mechanically, e.g. having frictionally-engaging springs as damping elements
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
- B60G13/14—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers accumulating utilisable energy, e.g. compressing air
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B66—HOISTING; LIFTING; HAULING
- B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
- B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
- B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
- B66F9/075—Constructional features or details
- B66F9/07513—Details concerning the chassis
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/20—Type of damper
- B60G2202/24—Fluid damper
Abstract
The invention provides a vibration damping mechanism of a fork lift truck, which is respectively arranged between a front cross beam and a front axle as well as between a rear cross beam and a rear axle, and comprises a pair of vibration damping oil cylinders arranged between two wings of the front cross beam and the front axle and a pair of vibration damping oil cylinders arranged between two ends of the rear cross beam and the rear axle; and second damping devices are arranged between the two feet of the front cross beam and the front axle and between the two feet of the rear cross beam and the rear axle. In the invention, because the second damping devices are arranged between the two feet of the front cross beam and the front axle and between the two feet of the rear cross beam and the rear axle, when the damping oil cylinder fails, the second damping devices can be used for damping, thereby meeting the requirements of users.
Description
Technical Field
The invention relates to a vibration reduction mechanism of a fork lift truck.
Background
The existing stacking machine utilizes a mode that a front bridge and a rear bridge support a front cross beam and a rear cross beam. The front cross member 100 supported by the front axle 101 has both ends in the shape of wings, and the rear cross member 200 supported by the rear axle 201 has the shape of a spindle.
The damping principle of the conventional stacking machine is that a beam is supported by a damping oil cylinder 1, the beam comprises a front beam 100 and a rear beam 200, and the front beam and the rear beam are supported at two ends of the front beam and the rear beam by a pair of damping oil cylinders 1 respectively; both ends of the front cross member 100 are supported by two shock-absorbing cylinders 1 at both ends on the front axle 101, and the rear cross member 200 is also supported by one shock-absorbing cylinder 1 at both ends on the rear axle 201, and the up-and-down vibration of the front and rear cross members is absorbed by compressing the four shock-absorbing cylinders 1, as shown in fig. 1 and 2.
Such a damping mechanism can not meet the needs of users if the damping cylinder 1 itself fails to have a poor damping effect.
Disclosure of Invention
Aiming at the defects that the shock absorption effect is poor and the requirements of users cannot be met if the shock absorption oil cylinder per se of the existing shock absorption mechanism fails, the invention provides the shock absorption mechanism of the fork lift truck.
The technical scheme adopted by the invention for realizing the technical purpose is as follows: a shock absorption mechanism of a fork lift truck is respectively arranged between a front cross beam and a front axle as well as between a rear cross beam and a rear axle and comprises a pair of shock absorption oil cylinders arranged between two wings of the front cross beam and the front axle and a pair of shock absorption oil cylinders arranged between two ends of the rear cross beam and the rear axle; and second damping devices are arranged between the two feet of the front cross beam and the front axle and between the two feet of the rear cross beam and the rear axle.
In the invention, because the second damping devices are arranged between the two feet of the front cross beam and the front axle and between the two feet of the rear cross beam and the rear axle, when the damping oil cylinder fails, the second damping devices can be used for damping, thereby meeting the requirements of users.
Further, in the above-described shock absorbing mechanism of a forklift: the second damping device is a disc-shaped damper.
Further, in the above-described shock absorbing mechanism of a forklift: the damping oil cylinder is a hydraulic oil cylinder without a rod cavity and is provided with an energy storage leather bag communicated with the damping oil cylinder.
Further, in the above-described shock absorbing mechanism of a forklift: the capacity of the energy storage leather bag is 1-3 liters.
Further, in the above-described shock absorbing mechanism of a forklift: the inner diameter of the cylinder barrel of the damping oil cylinder arranged between the rear cross beam and the rear axle is larger than 140 mm.
The present invention will be further described with reference to the accompanying drawings and detailed description.
Drawings
Fig. 1 is a damping mechanism (front) of the current fork lift truck.
Fig. 2 shows a damping mechanism (rear) of the current fork lift truck.
Fig. 3 is a shock absorbing mechanism (front) of a fork lift according to embodiment 1 of the present invention.
Fig. 4 shows a shock absorbing mechanism (rear) of a fork lift according to embodiment 1 of the present invention.
Detailed Description
Embodiment 1, this embodiment is a shock absorbing mechanism disposed between a front cross beam and a rear cross beam of a forklift and a front axle and a rear axle, as shown in fig. 3 and 4, the shock absorbing mechanism in this embodiment is respectively disposed between the front cross beam 100 and the front axle 101, and between the rear cross beam 200 and the rear axle 201, and includes a pair of shock absorbing cylinders 1 disposed between two wings 103 of the front cross beam 100 and the front axle 101, and a pair of shock absorbing cylinders 1 disposed between two ends of the rear cross beam 200 and the rear axle 201. The damping device comprises a pair of damping oil cylinders 1, and is characterized in that the total number of the damping oil cylinders 1 is 4, in practice, the damping oil cylinders 1 are hydraulic oil cylinders without rod cavities and are provided with energy storage leather bags 2 communicated with the hydraulic oil cylinders, and the inner diameters of cylinder barrels of the pair of damping oil cylinders 1, which are arranged between a front cross beam 100 and a front axle, are 90 mm; the capacity of the energy storage bladder 2 is 1.6 liters. The inner diameter of the cylinder barrel of a pair of shock absorption oil cylinders 1 arranged between the rear cross beam 200 and the rear axle 201 is 140mm, and the capacity of the energy storage leather bag 2 is 2 liters.
In this embodiment, in order to make the shock-absorbing cylinder 1 have shock-absorbing capacity when it is out of operation, a second shock-absorbing device 3 is further disposed between the two legs of the front cross member 100 and the front axle 101, and between the two legs of the rear cross member 200 and the rear axle 201. The second damping means 3 is a disc damper.
In the present embodiment, since the accumulator is used as an energy source, the state of change of the gas in the accumulatorCan be considered in terms of adiabatic variation, namely: p0V0 1.4＝P1V1 1.4＝P2V2 1.4Is a constant;
when the working pressure of the accumulator is from P1Down to P2Oil amount discharged: Δ V ═ V1—V2＝P0 0.71V0{(1/P2)0.71—(1/P1)0.71Due to normal no-load time P260bar, maximum operating pressure P1150bar, the total capacity of the accumulator is 1L, the charging pressure of the accumulator is 30bar, so the oil supply quantity delta V of the accumulator is 1x30.71{(1/6)0.71—(1/15)0.712.18x (0.275-0.142) ═ 0.29 (liter);
in the formula V0-the total capacity (L) of the accumulator; p1-representing the highest working pressure (Pa); p2-representing the lowest working pressure (Pa); p0-representing the pre-fueling charge pressure (Pa); v1-expression of pressure P1Gas volume (L) of time; v2-expression of pressure P2Gas volume (L) of time;
and the maximum discharge volume of hydraulic oil in the shock absorption oil cylinder is V (S (piston area) x H (piston rod stroke) 150cm when the working stroke of the piston rods of the front shock absorption oil cylinder and the rear shock absorption oil cylinder is 10mm20.225 liter and the maximum oil supplement amount of the energy accumulator are almost equal, and after the oil cylinder is used for one month or two months, the normal internal leakage of the oil seal further causes that the oil supplement amount of the energy accumulator can not meet the normal working stroke of the oil cylinder, so that the shock absorption oil cylinder fails, and the capacity of the shock absorption oil cylinder is effectively prolonged to be 1.6 liters.
Then the oil charge of the accumulator: Δ V ═ V1—V2＝P0 0.71V0{(1/P2)0.71—(1/P1)0.71Due to normal no-load time P240bar, maximum operating pressure P1100bar, the total capacity of the accumulator is 1.6L, the charging pressure of the accumulator is 50bar, so the oil supply amount Δ V of the accumulator is 1.6x50.71{(1/4)0.71— (1/10)0.71The maximum discharge volume of the hydraulic oil in the shock absorption oil cylinder is 0.896 (liter) which is 1.6x3.13(0.374-0.195), and the failure time of the shock absorption oil cylinder can be effectively prolonged.
The thrust that receives when the piston of rear axle shock absorber oil cylinder is static is:
f (thrust) P (pressure) x S (piston area) 110x1.02Kg/cm2 x63.6cm27124 kg. And the system pressurizing pressure is as follows:
f (charging pressure) x S (piston area) 120x1.02Kg/cm2 x63.6cm27784 kg. F (charging) and F (thrust) are not greatly different, so that when the shock-absorbing oil cylinder fails, the shock-absorbing oil cylinder is difficult to recover by only charging the system, and basically, the recovery can be finished by the aid of the balance weight of a jack. In addition, the maximum working pressure of the rear axle damping oil cylinder in a field test reaches 400bar which is greater than the factory test pressure of 300bar of the oil cylinder barrel, and the welding seam at the bottom of the oil cylinder barrel is squeezed and cracked due to overlarge pressure intensity to cause oil leakage. Now change into the cylinder that the internal diameter is 140mm, system's pressurized pressure is: f (charging pressure) x S (piston area) 120x1.02Kg/cm2 x150cm218360kg is much larger than F (thrust). Therefore, the shock absorption oil cylinder can be recovered by pressurizing the failed shock absorption piston rod by the system, and in addition, the maximum working pressure of the rear axle shock absorption oil cylinder in field test is 130bar, which is greatly smaller than the factory test pressure of 300bar of the oil cylinder barrel. The model selection of the oil cylinder is proved to meet the requirements.
In this embodiment, in order to reduce the load of the front and rear shock-absorbing cylinders, the service lives of the front and rear shock-absorbing cylinders are greatly prolonged, and the bearings and the piston rod heads of the shock-absorbing cylinders are protected under the condition that the shock-absorbing cylinders fail, the balance of the whole vehicle is ensured, and the tires are prevented from being worn eccentrically, and the second shock-absorbing devices 3 are further arranged between the two legs of the front cross beam 100 and the front axle 101 and between the two legs of the rear cross beam 200 and the rear axle 201. The specific modification scheme and test report is as follows:
the method comprises the steps of firstly moving a front axle assembly to the outside by using a special front axle dismounting trolley separation trolley body, determining the position of a front disc spring fixing seat by taking a specific riding bolt as a center according to the size requirement of the disc spring fixing seat and the shape and size science of an upper plate and a lower plate of a front axle, fixing each fixing seat by six M10X 1.5 fixing bolts, and finally placing a disc spring into the disc spring fixing seat (each fixing seat is provided with five disc springs).
A hole with the diameter of 55mm is arranged right above the selected specific riding bolt, the disc spring pressing plate on the disc spring shock absorber is well installed and fixed, and the position of the pressing plate can be adjusted to the central position of the disc spring due to the fact that the gap between the holes with the diameters of only 35mm and 55mm is 20 mm.
The front damping oil cylinders on two sides are installed to push the special trolley for the front axle to a proper position, the front damping oil cylinders and the rear damping oil cylinders are installed on the front axle, then the four-bar mechanism of the front axle is installed, and the pull rod of the cross beam is adjusted to the middle position. Thus, whether the disc spring pressing plate of the disc spring shock absorber is aligned with the disc spring fixed on the lower cross beam or not is determined, and otherwise, the position of the upper disc spring pressing plate is adjusted to the optimal position.
The rear axle counterweight is jacked and supported to a proper height by using a jack and an iron stool, the limiting supports of the rear steering axles on two sides are cut to a proper size according to the height of the disc spring fixing seat and the size of the disc spring pressing plate seat, and then the disc spring fixing seat is welded on a rear axle beam according to the size of the disc spring fixing seat.
And welding the disc spring pressing plate seat on the steering axle limiting support, and adding a reinforcing rib plate. Firstly, the disc spring supporting plate with the thickness of 8mm is placed in the disc spring fixing seat, and then the five disc springs are sequentially placed according to the combination mode of the disc springs. The rear shock absorption oil cylinders and the energy accumulator (the nitrogen charging pressure is 80bar) at two sides are arranged and accessories such as a pressure measuring port and the like are also arranged. Install the pressure plate seat to the dish spring clamp plate, slowly put down back counter weight with the jack, let the dish spring pressure plate press the dish spring of dish spring fixing base the inside (the back damping cylinder on both sides this moment is not atress), then according to following sixth point: and adjusting and testing the rear damping disc spring and the oil cylinder.
Proper energy accumulator and pressure measuring port are additionally arranged on front and rear shock absorption hydraulic oil paths
An energy accumulator and a pressure measuring port are arranged on the front damping hydraulic oil way: welding a fixed seat of the energy accumulator, then installing and fixing the 1.6L energy accumulator (the nitrogen charging pressure of the energy accumulator is 80bar), installing an oil pipe, a pressure measuring port and an oil stop valve, and screwing an oil locking valve of the front damping oil cylinder to the maximum opening degree.
Energy accumulator and pressure measuring port are installed on rear shock absorption hydraulic oil way
Welding a fixed seat of the energy accumulator, and then installing and fixing the energy accumulator with 1.6 liters (the nitrogen charging pressure of the energy accumulator is 80 bar); and installing an oil pipe, a pressure measuring port and an oil stop valve, and screwing an oil locking valve of the front damping oil cylinder to the maximum opening degree.
Adjusting a front damping disc spring and an oil cylinder:
a pressure measuring meter is connected to a pressure measuring port of the front damping oil cylinder, the front damping oil cylinders on two sides are jacked up by opening the oil inlet valve, and at the moment, the pressing plate of the disc spring is not in contact with the disc spring and then the oil inlet valve is closed. And (5) reading the pressure gauge of the front shock absorption oil cylinders on two sides to be 90-100 bar, and closing the engine.
And firstly, slowly opening the oil interception valve on the left to enable the front shock absorption oil cylinder on the left to slowly descend until the disc spring pressing plate is contacted with the disc spring, and observing the reading of the pressure measuring meter until the reading of the pressure measuring meter is about 40bar, closing the oil interception valve, and stopping descending the front shock absorption oil cylinder on the left. It is normal to measure the distance between the upper and lower beams with a vernier caliper within a range of 10-12 mm.
And then slowly opening the right oil interception valve to enable the right front damping oil cylinder to slowly descend until the disc spring pressing plate is contacted with the disc spring, observing the reading of the pressure measuring meter all the time, closing the oil interception valve until the reading of the pressure measuring meter is about 40bar, and stopping descending the right front damping oil cylinder at the moment. It is normal to measure the distance between the upper beam and the upper surface of the disc spring seat by a vernier caliper within 10 mm.
Because the distance of entablature and dish spring seat upper surface is 15mm when dish spring clamp plate just contacted dish spring, so the compressive capacity of the dish spring on both sides about this moment is: the supporting weight of the edge disc spring is calculated to be 6.5 tons according to a calculation formula of the disc spring when the thickness is 5 mm. According to the condition that F is PXS is 4x1000000x3.14x0.07x0.07 is 61544N is 6.15 tons, the weight of each support of the left front shock absorption oil cylinder and the right front shock absorption oil cylinder is calculated to be 6.15 tons; if the disc spring is not stressed, the weight supported by the left and right front shock absorption cylinders is F-PXS-9-1000000x3.14x0.07x0.07-138474N-13.85 tons. Therefore, after the disc spring shock absorber is added, the working load of a single oil cylinder is reduced by 7.7 tons. The load of the oil cylinder is obviously reduced, the service life of the oil cylinder can be effectively prolonged, and the reliability of the damping mechanism is greatly improved.
Adjusting a rear shock absorption disc spring and an oil cylinder:
and a pressure measuring meter is connected to a pressure measuring port of the rear damping oil cylinder, the oil inlet valve is opened, the rear damping oil cylinders on two sides are jacked up, and at the moment, the pressing plate of the disc spring is not in contact with the disc spring and then the oil inlet valve is closed. And (5) reading the pressure gauge of the rear shock absorption oil cylinder on two sides to be 80-90 bar, and closing the engine.
And firstly, slowly opening the oil interception valve on the left side to enable the rear shock absorption oil cylinder on the left side to slowly descend until the disc spring pressing plate is contacted with the disc spring, observing the reading of the pressure measuring meter all the time, closing the oil interception valve until the reading of the pressure measuring meter is about 40bar, and stopping descending the rear shock absorption oil cylinder on the left side. It is normal to measure the distance H of the scale from the upper surface of the disc spring seat with a caliper within the range of 39-40 mm.
And opening the oil inlet valve on the right slowly to enable the rear damping oil cylinder on the right to descend slowly until the disc spring pressing plate is contacted with the disc spring, observing the reading of the pressure measuring meter all the time, closing the oil inlet valve until the reading of the pressure measuring meter is about 40bar, and stopping descending the rear damping oil cylinder at the moment. It is normal to measure the distance H of the scale from the upper surface of the disc spring seat with a caliper within the range of 39-40 mm.
The compression amount of the disc spring at this time is: the support weight of the disc spring is 5.1 tons calculated according to a calculation formula of the disc spring at 4 mm. According to the formula that F is 4x1000000x3.14x0.07x0.07 is 61544N is 6.15 tons, the weight of the rear shock-absorbing oil cylinder support is calculated as follows: 6.15 tons; if the disc spring is not stressed, the weight supported by the left and right rear shock absorption cylinders is F-PXS-8 x1000000x3.14x0.07x0.07-123088N-12.3 tons. After the disc spring shock absorber is added, the working load of a single oil cylinder is reduced by 6.15 tons, the load of the oil cylinder is obviously reduced, the service life of the oil cylinder can be effectively prolonged, and the reliability of the shock absorption mechanism is greatly improved.
Claims (5)
1. A damping mechanism of a fork lift truck is respectively arranged between a front cross beam (100) and a front axle (101) and between a rear cross beam (200) and a rear axle (201), and comprises a pair of damping oil cylinders (1) arranged between two wings (103) of the front cross beam (100) and the front axle (101) and a pair of damping oil cylinders (1) arranged between two ends of the rear cross beam (200) and the rear axle (201); the method is characterized in that: and second damping devices (3) are arranged between the two feet of the front cross beam (100) and the front axle (101) and between the two feet of the rear cross beam (200) and the rear axle (201).
2. The shock absorbing mechanism of a forklift according to claim 1, wherein: the second damping device (3) is a disc-shaped damper.
3. The vibration reducing mechanism of a forklift according to claim 1 or 2, wherein: the damping oil cylinder (1) is a hydraulic oil cylinder without a rod cavity and is provided with an energy storage leather bag communicated with the damping oil cylinder.
4. The shock absorbing mechanism of a forklift according to claim 3, wherein: the capacity of the energy storage leather bag is 1-3 liters.
5. The shock absorbing mechanism of a forklift according to claim 3, wherein: the inner diameter of the cylinder barrel of the shock absorption oil cylinder (1) arranged between the rear cross beam (200) and the rear axle (201) is larger than 140 mm.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910679901.0A CN110588270A (en) | 2019-07-26 | 2019-07-26 | Vibration reduction mechanism of stacking machine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910679901.0A CN110588270A (en) | 2019-07-26 | 2019-07-26 | Vibration reduction mechanism of stacking machine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN110588270A true CN110588270A (en) | 2019-12-20 |
Family
ID=68852947
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910679901.0A Withdrawn CN110588270A (en) | 2019-07-26 | 2019-07-26 | Vibration reduction mechanism of stacking machine |
Country Status (1)
| Country | Link |
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| CN (1) | CN110588270A (en) |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2480190Y (en) * | 2001-04-17 | 2002-03-06 | 刘东升 | Vibration damping balance device |
| CN201472099U (en) * | 2009-09-03 | 2010-05-19 | 三一集团有限公司 | Container lifting vehicle |
| DE102009042576A1 (en) * | 2009-09-24 | 2011-03-31 | Benteler Automobiltechnik Gmbh | Device for active tracking |
| US20130234378A1 (en) * | 2012-03-09 | 2013-09-12 | Fox Factory, Inc. | Suspension damper |
| CN103640658A (en) * | 2013-12-07 | 2014-03-19 | 刘景物 | Shock absorption system for rear axle of electro-tricycle |
| CN105513479A (en) * | 2016-01-15 | 2016-04-20 | 浙江海洋学院 | Collision device with cushioning mechanism |
| CN109484992A (en) * | 2018-12-12 | 2019-03-19 | 盐田国际集装箱码头有限公司 | Trolley is transported in bridge dismounting lifting before a kind of stacker |
| CN210390671U (en) * | 2019-07-26 | 2020-04-24 | 盐田国际集装箱码头有限公司 | Vibration reduction mechanism of stacking machine |
-
2019
- 2019-07-26 CN CN201910679901.0A patent/CN110588270A/en not_active Withdrawn
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2480190Y (en) * | 2001-04-17 | 2002-03-06 | 刘东升 | Vibration damping balance device |
| CN201472099U (en) * | 2009-09-03 | 2010-05-19 | 三一集团有限公司 | Container lifting vehicle |
| DE102009042576A1 (en) * | 2009-09-24 | 2011-03-31 | Benteler Automobiltechnik Gmbh | Device for active tracking |
| US20130234378A1 (en) * | 2012-03-09 | 2013-09-12 | Fox Factory, Inc. | Suspension damper |
| CN103640658A (en) * | 2013-12-07 | 2014-03-19 | 刘景物 | Shock absorption system for rear axle of electro-tricycle |
| CN105513479A (en) * | 2016-01-15 | 2016-04-20 | 浙江海洋学院 | Collision device with cushioning mechanism |
| CN109484992A (en) * | 2018-12-12 | 2019-03-19 | 盐田国际集装箱码头有限公司 | Trolley is transported in bridge dismounting lifting before a kind of stacker |
| CN210390671U (en) * | 2019-07-26 | 2020-04-24 | 盐田国际集装箱码头有限公司 | Vibration reduction mechanism of stacking machine |
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| PB01 | Publication | ||
| PB01 | Publication | ||
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| WW01 | Invention patent application withdrawn after publication | ||
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Application publication date: 20191220 |