CN201627869U - Hydraulic buffer system - Google Patents
Hydraulic buffer system Download PDFInfo
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- CN201627869U CN201627869U CN 201020153249 CN201020153249U CN201627869U CN 201627869 U CN201627869 U CN 201627869U CN 201020153249 CN201020153249 CN 201020153249 CN 201020153249 U CN201020153249 U CN 201020153249U CN 201627869 U CN201627869 U CN 201627869U
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- hydraulic
- oil
- way valve
- solenoid valve
- lock chamber
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Abstract
The utility model relates to a hydraulic buffer system which comprises a hydraulic cylinder and an oil storage tank, wherein the hydraulic cylinder comprises a cylinder sleeve, a piston and a piston rod, wherein the piston slides inside the cylinder sleeve; and the piston divides the hydraulic cylinder into a buffer chamber and a lock chamber. The hydraulic buffer system further comprises a first one-way valve, a second one-way valve, a third one-way valve, a fourth one-way valve, a first hydraulic damper, a second hydraulic damper, a first solenoid valve and a second solenoid valve. The hydraulic buffer system has the advantages of smart design, simple and compact structure, low production cost, convenient maintenance after use in the vehicles and good buffering effect. The fixed-value hydraulic dampers that are arranged in the oil drainage passage fulfill the function of providing the resistance in direct proportion to the turning speed of the vehicle. The solenoid valves control the on/off of the oil passage of the lock chamber, so that the vehicle has both the over-angle locking function and the straight movement restoration function.
Description
Technical field
The utility model relates to vehicle with damping shock absorption control system technical field, relates in particular to a kind of hydraulic buffer system.
Background technique
Along with developing rapidly of China auto manufacturing, various vehicle manufacturing industry are also being advanced by leaps and bounds, and characteristics such as articulated bus is big with its handling capacity of passengers, utilization factor height big and medium-sized cities at home obtain promoting gradually.Articulated coach generally is made up of the chassis articulated system in compartment before and after compartment, front and back and the connection, wherein the hydraulic buffer system in the articulated system of chassis is the key factor of restriction articulator performance, in the prior art, the hydraulic buffer system of articulated coach is generally by two oil hydraulic cylinders, hydraulic controller and electric control system are formed, oil hydraulic cylinder is by the size of its output resistance of hydraulic controller control change, electric control system is according to the turn inside diameter angle, signal to hydraulic controller, make the different force value of its conversion, disclose a kind of the rotation as Chinese patent CN201086607 and controlled hydraulic damping by mandrel, thereby the damping of conversion buffering hydraulic control system, though this control system can form different dampings according to the variation of vehicle angle, before preventing, back car shearing aspect plays positive effect, but the mandrel structure is complicated, the requirement on machining accuracy height, cost is higher, it is miscellaneous that connection is installed, and it is big to take up room, and also leakage of oil can occur, shortcomings such as the stuck or electrical malfunction of spool.
Simultaneously, because buffering damping of the prior art can not be precisely controlled, the driver during particularly big turning, tends to have an accident because angle of turn is much when driving articulator, causes personnel's the injures and deaths and the loss of property.
The model utility content
The purpose of this utility model is to have overcome above-mentioned shortcoming of the prior art, a kind of simple and practical hydraulic buffer system is provided, the utility model designs compactness ingenious, simple for structure, cost of production is low, easy to maintenance, good buffer effect, by being provided with the definite value hydraulic damping, play the resistance buffer function that is directly proportional with turn inside diameter speed, the function that makes vehicle possess super angle locking and recover to keep straight on simultaneously.
To achieve these goals, the utility model provides a kind of hydraulic buffer system, comprise oil hydraulic cylinder and fuel reserve tank, described oil hydraulic cylinder comprises cylinder sleeve, piston and piston rod, described piston slides in described cylinder sleeve, described piston rod one end connects described piston, described piston is divided into buffer cavity and lock chamber with oil hydraulic cylinder, described hydraulic buffer system also comprises first one-way valve, second one-way valve, the 3rd one-way valve, the 4th one-way valve, first hydraulic damping, second hydraulic damping and first solenoid valve and second solenoid valve; Described buffer cavity and described first hydraulic damping, first one-way valve and described fuel reserve tank are composed in series the oil extraction oil circuit successively, and described buffer cavity and described the 3rd one-way valve and fuel reserve tank are composed in series oil suction line successively; Described lock chamber and described second hydraulic damping, second one-way valve, second solenoid valve and fuel reserve tank are composed in series the oil extraction oil circuit successively; Described lock chamber and described the 4th one-way valve, first solenoid valve and fuel reserve tank form successively and are composed in series oil suction line.
Described hydraulic buffer system also comprise first near switch and second near switch, described first is electrically connected with described first solenoid valve near switch, described second is electrically connected with described second solenoid valve near switch.
Described fuel reserve tank is arranged on the outside of described oil hydraulic cylinder cylinder sleeve.
Described oil hydraulic cylinder also comprises lock chamber integrated package and buffering cavity rear end lid, and described lock chamber integrated package and buffering cavity rear end lid are located at the sealed at both ends described cylinder sleeve of cylinder sleeve respectively, and described piston rod one end connects piston, and the other end passes described lock chamber integrated package.
Preferably, described first one-way valve, the 3rd one-way valve and first hydraulic damping are arranged on the buffer cavity rear end cover; Described first solenoid valve, second solenoid valve, second one-way valve, the 4th one-way valve, second hydraulic damping and oil suction filler opening are arranged in the described lock chamber integrated package, and be simple and compact for structure.
The utlity model has following beneficial effect:
1. pressure control is simple, does not need electrical control or rotational valve core can produce the buffering resistance, can not occur leakage of oil basically, spool is stuck and electrical malfunction etc., greatly reduces rate of fault; Simultaneously can provide the hydraulic cushion that is directly proportional with turn inside diameter speed power.
2. low cost of manufacture need not used expensive hydraulic proportion valve or make the high rotary valve of machining accuracy, greatly reduces manufacture cost, has improved the competitive ability on market.
3. simple in structure, have good interchangeability, especially in articulated coach, left hydraulic cylinder and right oil hydraulic cylinder be symmetry each other, and other structures and components and parts are just the same.
4. easy to install and use, after hydraulic buffer system assembling is finished and refueled through unique oiling technology, be installed on the articulated system easily, only need be installed to oil cylinder on the frame, do not need other to be installed again as oil pipe, component such as pipe joint.
Description of drawings:
Fig. 1 is to use chassis of the present utility model articulated system assembly plan view.
Fig. 2 is the utility model hydraulic buffer system oil circuit control principle system diagram.
Fig. 3 a the utility model hydraulic buffer system assembly sectional view.
Fig. 3 b the utility model hydraulic buffer system assembly schematic perspective view.
Fig. 4 is that Fig. 3 a is about the buffer cavity rear end cover schematic perspective view in the utility model hydraulic buffer system assembly.
Fig. 5 a is that Fig. 3 a is about the lock chamber integrated package schematic perspective view in the utility model hydraulic buffer system assembly.
Fig. 5 b is another schematic perspective view of Fig. 5 a lock chamber integrated package.
Embodiment:
In order more to be expressly understood technology contents of the present utility model, describe in detail especially exemplified by following examples.
As Fig. 1-shown in Figure 5, the utility model relates to a kind of hydraulic buffer system, comprise: three chambeies (comprise buffer cavity 2, lock chamber 3 and fuel reserve tank 4), two controls (comprising first solenoid valve 41 and second solenoid valve 42), two hydraulic dampings (first hydraulic damping 21 and second hydraulic damping 22), four cylinder sleeves that one-way valve and conventional oil hydraulic cylinder had 14, piston 5, piston rod 6, seal ring etc.Described piston 5 slidably is arranged in the oil hydraulic cylinder 1, and oil hydraulic cylinder is divided into buffer cavity 2 and lock chamber 3, and described piston 5 is fixedlyed connected with piston rod 6;
Described buffer cavity 2 is connected with first hydraulic damping 21, first one-way valve 31 and fuel reserve tank 4 oil circuit successively, forms the oil extraction oil circuit, and described buffer cavity 2 also is composed in series oil suction line successively with the 3rd one-way valve 33 and fuel reserve tank 4; Described lock chamber 3 and second hydraulic damping 22, second one-way valve 32, second solenoid valve 42 and fuel reserve tank 4 are composed in series the oil extraction oil circuit successively, and described lock chamber 3 also is composed in series oil suction line successively with the 4th one-way valve 34, first solenoid valve 41 and fuel reserve tank 4; The resistance buffer function that described first hydraulic damping and second hydraulic damping can make compression speed be directly proportional with the damping reaction.。
Preferably, described hydraulic buffer system also comprise first near switch and second near switch, described first is electrically connected with described first solenoid valve 41 near switch, described second is electrically connected with described second solenoid valve 42 near switch, more preferably, described first is inductive switch near switch and described second near switch.
Preferably, described fuel reserve tank 4 is arranged on the outside of described cylinder sleeve 14.
Preferably, described oil hydraulic cylinder 1 also comprises lock chamber integrated package 11 and buffering cavity rear end 12, and is located at the two ends of the cylinder sleeve 14 of described oil hydraulic cylinder 1 respectively, seals described cylinder sleeve 14, and described piston rod 6 one ends connect piston 5, and the other end passes described lock chamber integrated package 11.
Preferably, as shown in Figure 3-Figure 5, described first one-way valve 31, the 3rd one-way valve 33 and first hydraulic damping 21 are arranged on the buffer cavity rear end cover 12; Described first solenoid valve 31, second solenoid valve 32, second one-way valve 32, the 4th one-way valve 34, second hydraulic damping 22 and oil suction filler opening 50 are arranged on the described lock chamber integrated package 11.
As Fig. 2, shown in Figure 3, when oil hydraulic cylinder 1 power contraction by compression, piston 5 moves to buffer cavity 2, in buffer cavity 2, hydraulic oil by compression, pressure is with speed by compression or increase soon or slowly, and through first hydraulic damping 21 time, hydraulic oil is discharged more or less, the compressive force that oil hydraulic cylinder 1 is subjected to is big more, shrink soon more, the oil mass of need discharging is just many more, and the resistance that oil hydraulic cylinder 1 produces is just big more, after producing pressure difference through first hydraulic damping 21, hydraulic oil is opened first one-way valve 31 and is got back to fuel reserve tank 4; At lock chamber 3, because piston 5 moves to left, lock chamber 3 volumes increase, and cause vacuum, and the oil in the fuel reserve tank 4 is through solenoid valve 41 and one-way valve 34, and vacuum is eliminated in repairing in the past lock chamber 3, guarantees that the oil in the lock chamber 3 is full state; Because fuel reserve tank 4 is to be in atmospheric pressure state, therefore the pressure difference of first hydraulic damping, 21 generations is the pressure in the oil hydraulic cylinder 1, and this pressure makes oil hydraulic cylinder overcome the compressive force of external force to its generation, makes piston 6 get back to the neutral position.When the external force continuous action surpasses the scope of setting, piston 5 moves left to certain position, first is opened near switch, and first solenoid valve 41 is closed, and the oil in the fuel reserve tank 4 can not flow in the lock chamber 3, lock chamber 3 forms negative pressure of vacuum, stop piston 5 to continue to move to left, but solenoid valve 42 open, owing to the reason of pressure difference, piston 5 can move to right and reset, and finishes the damping buffering effect.
When oil hydraulic cylinder 1 stretches, piston 5 moves to lock chamber 3, in lock chamber 3, hydraulic oil is power by compression, and pressure increases gradually, and hydraulic oil is also with the increase of pressure, the hydraulic oil of discharging increases, hydraulic oil is through second hydraulic damping 22, and after the generation pressure difference, hydraulic oil is opened second one-way valve 32 and got back to fuel reserve tank 4; At buffer cavity 2, because piston 5 moves to right, buffer cavity 2 volumes increase, and the oil in the fuel reserve tank 4 is through the 3rd one-way valve 33, and repairings in the buffer cavity 2 guarantee that the oil in the buffer cavity 2 are full state, and in like manner because pressure difference, piston 6 also can be got back to the neutral position.When scope that the external force continuous action surpass to be set, piston 5 is shifted to the right to certain position, and second is opened near switch, second solenoid valve 42 is closed, hydraulic oil in the lock chamber 3 can not be back in the fuel reserve tank 4, because the incompressibility of liquid stops piston 5 to continue to move to right, finish locking, but solenoid valve 41 is opened, and under action of pressure, piston 5 can move to left and reset, get back to the neutral position of oil hydraulic cylinder 1, finish the effect of buffering damping.
In the reality, first can be provided with in place as required near the switch and second position near switch, in the present embodiment, first is arranged on after-frame assembly 10 and side arm assembly 9 joints near switch and second near switch, be subjected to the electric control system controls outside this hydraulic buffer system, when piston 5 was positioned at the neutral position and is not triggered near switch, first solenoid valve 41 and second solenoid valve 42 all were in open mode; Flexible during to certain position when oil cylinder, making by circuit control in two solenoid valves of hydraulic buffer system to have a solenoid valve energising, disconnects oil circuit, to mobile the carry out locking of piston 5 to a certain direction.
Further, the hydraulic damping system of articulated coach uses the left hydraulic cylinder 7 and the right oil hydraulic cylinder 8 of symmetry each other, left hydraulic cylinder 7 is connected side arm assembly 9 and after-frame assembly 10 respectively with right oil hydraulic cylinder 8 two ends, work as Ackermann steer angle, must there be an oil hydraulic cylinder to stretch, and another oil hydraulic cylinder compression (as shown in Figure 1).When articulator is kept straight on, the piston of left hydraulic cylinder 7 and right oil hydraulic cylinder 8 all is in the neutral position, this moment, the buffer cavity and the lock chamber of oil hydraulic cylinder all were full of hydraulic oil, when vehicle turns left, left hydraulic cylinder 7 is compressed power and shrinks, right oil hydraulic cylinder 8 is subjected to tensile force and stretches out, and its oil circuit control does not repeat them here; When the angle of vehicle left-hand bend surpasses the scope of setting, vehicle electrically controlling system is by triggering near switch, give the solenoid valve 41 of left hydraulic cylinder 7 of buffer system and solenoid valve 42 power supplies of right oil hydraulic cylinder 8, the solenoid valve 41 of left hydraulic cylinder 7 and the solenoid valve 42 of right oil hydraulic cylinder 8 commutate to off state, the fuel reserve tank that stops left hydraulic cylinder 7 is toward the lock chamber repairing, stop the oil in right oil hydraulic cylinder 8 lock chambers to flow out simultaneously, like this, reason owing to pressure difference, left hydraulic cylinder 7 can only stretch out, and can not further shrink; Right oil hydraulic cylinder 8 can only shrink, and can not further stretch out, and vehicle can only be replied toward the craspedodrome direction, can not continue to strengthen the angle of turning, guarantees that vehicle can not have an accident because angle of turn is excessive, guarantees that simultaneously vehicle can be returned to the craspedodrome state.
When vehicle was turned right, the left hydraulic cylinder 7 of hydraulic damping system was subjected to tensile force and stretches out, and right oil hydraulic cylinder 8 is compressed power and shrinks, and asphalt principle is identical with left-hand bend.Different is, when the angle of turning right surpasses the scope of setting, vehicle electrically controlling system is by triggering near switch, give solenoid valve 41 power supplies of the solenoid valve 42 and the right oil hydraulic cylinder 8 of left hydraulic cylinder 7, the solenoid valve 42 of left hydraulic cylinder 7 and the solenoid valve 41 of right oil hydraulic cylinder 8 commutate to off state, and vehicle can only be replied toward the craspedodrome direction, can not continue to strengthen the angle of turning, guarantee that vehicle can not meet accident because angle of turn is excessive, guarantee that simultaneously vehicle can be returned to the craspedodrome state.
Four one-way valves guarantee to be full of fluid in buffer cavity 2 and the lock chamber 3, guarantee buffer cavity 2 and lock chamber 3 simultaneously from fuel reserve tank 4 oil suctions, and oil circuit is smooth and easy during toward fuel reserve tank 4 oil extractions; By first hydraulic damping and second hydraulic damping that in the oil extraction oil circuit, is provided with, play the resistance buffer function that the damping reaction in the oil hydraulic cylinder is directly proportional with turn inside diameter speed; Like this, no matter be to turn left or right-hand bend, buffer system stops vehicle to continue to strengthen the angle of turning, and makes vehicle possess super angle locking and the function of recovering to keep straight on simultaneously.
As shown in Figure 3-Figure 5, oil-discharging circuit at buffer cavity and lock chamber is provided with the definite value hydraulic damping, when vehicle is kept straight on, oil cylinder piston is in the neutral position, work as Ackermann steer angle, when oil hydraulic cylinder is stretched by external force, the lock chamber of oil hydraulic cylinder or buffer cavity must oil extractions, just flexible of oil hydraulic cylinder, and during the oil hydraulic cylinder oil extraction, pressure difference between oil-discharging cavity (lock chamber or buffer cavity) and the fuel reserve tank is to be directly proportional with the flow of oil extraction, just be directly proportional,, just produce pressure difference as long as the turn inside diameter piston moves with the speed of turn inside diameter, like this, oil cylinder is just to having produced the effect of external mechanical resistance power buffering.The position of hydraulic damping is most possibly in the top of oil cylinder, and what at first discharge when guaranteeing oil extraction is air, and two chambeies (lock chamber and buffer cavity) of final oil hydraulic cylinder all are full of fluid; Simultaneously, in the extreme lower position (as described above) of oil hydraulic cylinder, when guaranteeing oil suction, fluid is oil suction under liquid level always most possibly for oil suction filler opening 50, avoids hydraulic oil to produce bubble, causes undesirable elements such as resistance instability.The size of the resistance that the definite value hydraulic damping produces is directly proportional with the flow of oil extraction, and promptly the speed of Ackermann steer angle is fast more, and the oil extraction flow is big more, and the resistance that oil hydraulic cylinder produces is just big more.Different vehicles according to the size of required resistance, is used the hydraulic damping of different sizes.
To sum up, hydraulic buffer system of the present utility model designs compactness ingenious, simple for structure, cost of production is low, easy to maintenance, good buffer effect, can be by being provided with the definite value hydraulic damping, play the resistance buffer function that is directly proportional with speed, the function that makes vehicle possess super angle locking and recover to keep straight on simultaneously.
In this specification, the utility model is described with reference to its certain embodiments.But, still can make various modifications and conversion obviously and not deviate from spirit and scope of the present utility model.Therefore, specification and accompanying drawing are regarded in an illustrative, rather than a restrictive.
Claims (5)
1. hydraulic buffer system, comprise oil hydraulic cylinder and fuel reserve tank, described oil hydraulic cylinder comprises cylinder sleeve, piston and piston rod, described piston slides in described cylinder sleeve, described piston is divided into buffer cavity and lock chamber with oil hydraulic cylinder, it is characterized in that: described hydraulic buffer system also comprises first one-way valve, second one-way valve, the 3rd one-way valve, the 4th one-way valve, first hydraulic damping, second hydraulic damping and first solenoid valve and second solenoid valve; Described buffer cavity and described first hydraulic damping, first one-way valve and described fuel reserve tank are composed in series the oil extraction oil circuit successively, described buffer cavity and described the 3rd one-way valve and fuel reserve tank are composed in series oil suction line successively, described lock chamber and described second hydraulic damping, second one-way valve, second solenoid valve and fuel reserve tank are composed in series the oil extraction oil circuit successively, and described lock chamber and described the 4th one-way valve, first solenoid valve and fuel reserve tank are composed in series oil suction line successively.
2. hydraulic buffer system according to claim 1, it is characterized in that: described hydraulic buffer system also comprise first near switch and second near switch, described first is electrically connected with described first solenoid valve near switch, and described second is electrically connected with described second solenoid valve near switch.
3. hydraulic buffer system according to claim 1 is characterized in that: described fuel reserve tank is arranged on the outside of described cylinder sleeve.
4. according to the described hydraulic buffer system of arbitrary claim among the claim 1-3, it is characterized in that: described oil hydraulic cylinder also comprises lock chamber integrated package and buffering cavity rear end lid, and described lock chamber integrated package and buffering cavity rear end lid are located at the sealed at both ends described cylinder sleeve of described cylinder sleeve respectively.
5. hydraulic buffer system according to claim 4 is characterized in that: described first one-way valve, the 3rd one-way valve and first hydraulic damping are arranged on the described buffer cavity rear end cover; Described first solenoid valve, second solenoid valve, second one-way valve, the 4th one-way valve, second hydraulic damping and oil suction filler opening are arranged in the described lock chamber integrated package.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201020153249 CN201627869U (en) | 2010-03-29 | 2010-03-29 | Hydraulic buffer system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201020153249 CN201627869U (en) | 2010-03-29 | 2010-03-29 | Hydraulic buffer system |
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| CN201627869U true CN201627869U (en) | 2010-11-10 |
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| CN 201020153249 Expired - Lifetime CN201627869U (en) | 2010-03-29 | 2010-03-29 | Hydraulic buffer system |
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102102728A (en) * | 2010-03-29 | 2011-06-22 | 伊卡露斯(苏州)车辆系统有限公司 | Hydraulic buffer system |
| CN102152719A (en) * | 2011-02-15 | 2011-08-17 | 伊卡路斯(苏州)车辆系统有限公司 | Damping control buffering system with high integration |
| CN102161301A (en) * | 2010-11-30 | 2011-08-24 | 伊卡路斯(苏州)车辆系统有限公司 | Articulated system of articulated vehicle chassis |
| CN103161869A (en) * | 2012-09-07 | 2013-06-19 | 伊卡路斯(苏州)车辆系统有限公司 | Infinite damping shock absorption system |
| CN103195855A (en) * | 2013-04-28 | 2013-07-10 | 伊卡路斯(苏州)车辆系统有限公司 | Hydraulic buffer system for rotary dampers |
| CN107806483A (en) * | 2017-11-13 | 2018-03-16 | 西南交通大学 | A kind of camshaft speed hydraulic pressure attenuator |
| EP3208488A4 (en) * | 2014-10-16 | 2018-07-18 | Jointech (Suzhou) Vehicle System Co., Ltd. | Articulated system-based hydraulic buffer for realizing safe turn-back of vehicle, and method therefor |
-
2010
- 2010-03-29 CN CN 201020153249 patent/CN201627869U/en not_active Expired - Lifetime
Cited By (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102102728A (en) * | 2010-03-29 | 2011-06-22 | 伊卡露斯(苏州)车辆系统有限公司 | Hydraulic buffer system |
| CN102161301A (en) * | 2010-11-30 | 2011-08-24 | 伊卡路斯(苏州)车辆系统有限公司 | Articulated system of articulated vehicle chassis |
| CN102161301B (en) * | 2010-11-30 | 2013-04-03 | 伊卡路斯(苏州)车辆系统有限公司 | Articulated system of articulated vehicle chassis |
| CN102152719A (en) * | 2011-02-15 | 2011-08-17 | 伊卡路斯(苏州)车辆系统有限公司 | Damping control buffering system with high integration |
| CN102152719B (en) * | 2011-02-15 | 2012-09-19 | 伊卡路斯(苏州)车辆系统有限公司 | Damping control buffering system with high integration |
| CN103161869A (en) * | 2012-09-07 | 2013-06-19 | 伊卡路斯(苏州)车辆系统有限公司 | Infinite damping shock absorption system |
| CN103161869B (en) * | 2012-09-07 | 2015-04-01 | 伊卡路斯(苏州)车辆系统有限公司 | Infinite damping shock absorption system |
| CN103195855A (en) * | 2013-04-28 | 2013-07-10 | 伊卡路斯(苏州)车辆系统有限公司 | Hydraulic buffer system for rotary dampers |
| CN103195855B (en) * | 2013-04-28 | 2015-05-20 | 伊卡路斯(苏州)车辆系统有限公司 | Hydraulic buffer system for rotary dampers |
| EP3208488A4 (en) * | 2014-10-16 | 2018-07-18 | Jointech (Suzhou) Vehicle System Co., Ltd. | Articulated system-based hydraulic buffer for realizing safe turn-back of vehicle, and method therefor |
| CN107806483A (en) * | 2017-11-13 | 2018-03-16 | 西南交通大学 | A kind of camshaft speed hydraulic pressure attenuator |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| C56 | Change in the name or address of the patentee | ||
| CP01 | Change in the name or title of a patent holder |
Address after: 215211 Wujiang City, Jiangsu province FENHU Economic Development Zone, the community Fen Road No. 666 Patentee after: Jointech (Suzhou) Vehicle System Co., Ltd. Address before: 215211 Wujiang City, Jiangsu province FENHU Economic Development Zone, the community Fen Road No. 666 Patentee before: Jointech Vehicle System (Suzhou) Co., Ltd. |
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| AV01 | Patent right actively abandoned |
Granted publication date: 20101110 Effective date of abandoning: 20120725 |