CN203066069U - Pipe winding device hydraulic system and piling machinery - Google Patents
Pipe winding device hydraulic system and piling machinery Download PDFInfo
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- CN203066069U CN203066069U CN 201220739246 CN201220739246U CN203066069U CN 203066069 U CN203066069 U CN 203066069U CN 201220739246 CN201220739246 CN 201220739246 CN 201220739246 U CN201220739246 U CN 201220739246U CN 203066069 U CN203066069 U CN 203066069U
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- tube rolling
- variable pump
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Abstract
The utility model discloses a pipe winding device hydraulic system and piling machinery. The pipe winding device hydraulic system comprises a variable pump, a proportional control valve set and pipe winding device motors. A first oil port of the variable pump is connected to lifting oil ports of the pipe winding device motors. An oil inlet and an oil outlet of the proportional control valve set are respectively connected to the first oil port of the variable pump and a variable piston cylinder of the variable pump. Therefore, a negative feedback channel of the variable pump is formed. When the pressure of oil of the first oil port of the variable pump reaches a preset value in the proportional control valve set, the proportional control valve set acts on the variable piston cylinder. According to the pipe winding device hydraulic system, the tension force born by main oil pipes can be changed, the tension force born by the main oil pipes is fit with the depth where the main oil pipes are located, namely the main oil pipes are prevented from bearing the maximum tension force at any depth. The service lives of the main oil pipes are prolonged. Therefore, construction cost is reduced.
Description
Technical field
The utility model relates to tube rolling device control technology field, particularly a kind of tube rolling device hydraulic system and piling machinery.
Background technology
Deep foundation piling machinerys such as continuous wall hydraulic grab, reaming rig generally are made up of chassis, equipment etc. at present.In work progress, in order to realize the reciprocating action of equipment, need realize oil-feed and oil return by two hydralic hoses (claiming left and right sides main oil pipe again) on two tube rolling devices about being wrapped in respectively, particularly, wherein hydralic hose is transferred to equipment with the high-pressure and hydraulic oil of chassis main pump output, and another root hydralic hose provides drainback passage for equipment.
Because two hydralic hoses need in depth carry out construction operation down with equipment, along with the lifting of equipment/transfer, about two tube rolling devices propose/transfer operation on need carrying out thereupon, realize that pipe is managed/put to the receipts of main oil pipe, to guarantee the follow-up motion of main oil pipe and equipment.Existing tube rolling device hydraulic system generally adopts the constant displacement pump open type hydraulic system, during lifting, the tube rolling device hydraulic system has maximum constant lifting oil pressure relief, mention with the tube rolling device moment of torsion that guarantees the output of this pressure main oil pipe can be with maximum construction depth the time, and make main oil pipe bear bigger permanent tension force constantly, also guaranteed the synchronous of main oil pipe and equipment; When transferring, equipment is being dragged main oil pipe and is being transferred synchronously, and the tube rolling device hydraulic system has constant overflow back pressure.
Existing tube rolling device hydraulic system exists following deficiency or defective: owing to promoting/when transferring, the set pressure of hydraulic system is a bigger steady state value, make main oil pipe all bear maximum tensile force in any degree of depth, in the application life of having reduced main oil pipe, increased construction cost; In addition, owing to adopt constant displacement pump, promote at equipment (left and right sides main oil pipe)/when transferring, there is spill losses in hydraulic system always, and system effectiveness is low.
The utility model content
In view of this, the utility model is intended to propose a kind of tube rolling device hydraulic system and piling machinery, setting value by the proportional control valve group in the control tube rolling device hydraulic system, can change the size of the tensile force that main oil pipe bears, the tensile force that main oil pipe the is born degree of depth residing with it adapts, thereby improves the application life of main oil pipe.
On the one hand, the utility model provides a kind of tube rolling device hydraulic system, and described tube rolling device hydraulic system comprises variable pump, proportional control valve group and tube rolling device motor; First hydraulic fluid port of described variable pump be connected to described tube rolling device motor on carry hydraulic fluid port; The oil inlet and outlet of described proportional control valve group is connected to first hydraulic fluid port of described variable pump and the variable piston rod of described variable pump respectively, thereby forms the negative feedback channel of described variable pump; The fluid of first hydraulic fluid port of described variable pump acts on described variable piston rod through described proportional control valve group when its pressure reaches the setting value of described proportional control valve group.
Further, described variable pump is the enclosed variable pump, first hydraulic fluid port of described variable pump be connected to described tube rolling device motor on carry hydraulic fluid port, second hydraulic fluid port of described variable pump is connected to the following fuel outlet of described tube rolling device motor.
Further, described tube rolling device motor comprises the first tube rolling device motor and the second tube rolling device motor; Described tube rolling device hydraulic system also comprises the synchronous control valve group; First hydraulic fluid port of described variable pump by described synchronous control valve be connected to the described first tube rolling device motor and the described second tube rolling device motor on carry hydraulic fluid port, second hydraulic fluid port of described variable pump is connected to the following fuel outlet of the described first tube rolling device motor and the described second tube rolling device motor by described synchronous control valve.
Further, the oil circuit between first hydraulic fluid port of described proportional control valve group and described variable pump is provided with reversal valve and/or first throttle valve.
Further, described proportional control valve group is ratio sequence valve group or proportional reversing valve group.
Further, described ratio sequence valve group comprises sequence valve and first overflow valve; Described sequence valve is hydraulically-controlled type, and described first overflow valve is proportion magnetic valve; The oil-in of described sequence valve is connected to first hydraulic fluid port of described variable pump, the oil-out of described sequence valve is connected to the variable piston rod of described variable pump, first hydraulic control of described sequence valve is terminated at the oil-in of described sequence valve, the second hydraulic control end of described sequence valve is connected to the oil-in of described sequence valve and the oil-in of described first overflow valve simultaneously, and the overfall of described first overflow valve is connected to fuel tank.
Further, described ratio sequence valve group also comprises second choke valve and the 3rd choke valve; The oil-in of described sequence valve and the second hydraulic control end are connected to the oil-in of described first overflow valve respectively by described first throttle valve and described second choke valve.
Further, described ratio sequence valve group also comprises second overflow valve, and the oil-in of described second overflow valve is connected to the oil-out of described sequence valve, and the overfall of described second overflow valve is connected to fuel tank.
Further, described ratio sequence valve group also comprises the 4th choke valve, and described the 4th choke valve is arranged at the oil-out of described sequence valve to the oil circuit between the described variable piston rod.
Another utility model, the utility model also provide a kind of piling machinery, and this piling machinery is provided with above-mentioned each described tube rolling device hydraulic system.
Tube rolling device hydraulic system of the present utility model in use, can be by (pressure) setting value of control ratio control valve group, for example can make this setting value and main oil pipe transfer the proportional synchronous increase of the degree of depth or minimizing, when promoting, if the receipts pipe speed of tube rolling device is greater than the hoisting velocity of equipment, main oil pipe will be pulled to hypercompact state, at this moment, system pressure (being the pressure of variable pump first hydraulic fluid port) reaches the setting value of proportional control valve group, the proportional control valve group is opened, the fluid of variable pump first hydraulic fluid port is with the variable piston rod of passing ratio control valve group effect to variable pump, the variable pump delivery reduces, the receipts pipe speed of tube rolling device slows down, and main oil pipe is fluffed by hypercompact state and is the corresponding rate of tension of the setting value of proportional control valve group; If the receipts pipe speed of tube rolling device is lower than the hoisting velocity of equipment, main oil pipe will be in relaxed state, at this moment, system pressure is less than the setting value of proportional control valve group, the proportional control valve group is closed, and feedback effect is not to the variable piston rod for the fluid of variable pump first hydraulic fluid port, and the variable pump delivery increases, tube rolling device is received pipe fast, reaches the rate of tension of the setting value correspondence of proportional control valve group until main oil pipe; Compared with prior art, tube rolling device hydraulic system of the present utility model can change the size of the tensile force that main oil pipe bears, the tensile force that main oil pipe the is born degree of depth residing with it adapts, namely avoided main oil pipe all bearing maximum tensile force in any degree of depth, improve the application life of main oil pipe, thereby reduced construction cost.
Piling machinery of the present utility model is provided with above-mentioned tube rolling device hydraulic system, because above-mentioned tube rolling device hydraulic system has above-mentioned technique effect, therefore, this piling machinery also has corresponding technique effect.
Description of drawings
The accompanying drawing that constitutes a part of the present utility model is used to provide further understanding of the present utility model, and illustrative examples of the present utility model and explanation thereof are used for explaining the utility model, do not constitute improper restriction of the present utility model.In the accompanying drawings:
The structural representation of a kind of tube rolling device hydraulic system that Fig. 1 provides for the utility model embodiment;
Fig. 2 is the hydraulic principle schematic diagram of a kind of specific embodiment of tube rolling device hydraulic system shown in Figure 1.
The critical element symbol description:
1 motor
2 variable pumps
3 synchronous control valve groups
4 proportional control valve groups
5 first tube rolling devices
6 second tube rolling devices
7 first tube rolling device motors
8 second tube rolling device motors
9 ratio sequence valve groups
11 sequence valves
12 second choke valves
13 the 3rd choke valves
14 first overflow valves
15 second overflow valves
16 the 4th choke valves
17 first throttle valves
18 reversal valves
The specific embodiment
Should be pointed out that in this part that to the description of concrete structure and description order only be explanation to specific embodiment, should not be considered as that protection domain of the present utility model is had any restriction.In addition, under the situation of not conflicting, embodiment and the feature among the embodiment in this part can make up mutually.
Please refer to Fig. 1 and Fig. 2, elaborate below in conjunction with the utility model of embodiment.
In conjunction with shown in Figure 1, the tube rolling device hydraulic system of this embodiment comprises variable pump 2, synchronous control valve group 3, proportional control valve group 4, the first tube rolling device motor 7 and the second tube rolling device motor 8.For the convenience of describing, be convenient to public understanding simultaneously, motor 1, first tube rolling device 5 and second tube rolling device 6 also are shown among the figure; But should be noted that the hydraulic system that the utility model embodiment provides can not comprise motor 1, first tube rolling device 5 and second tube rolling device 6.
Wherein, the power output shaft of motor 1 drives with the power input shaft of variable pump 2 and is connected; Variable pump 2 is the enclosed variable pump, the first hydraulic fluid port A of variable pump 2 by synchronous control valve be connected to the first tube rolling device motor 7 and the second tube rolling device motor 8 on carry hydraulic fluid port, the second hydraulic fluid port B of variable pump 2 is connected to the following fuel outlet of the first tube rolling device motor 7 and the second tube rolling device motor by synchronous control valve.
The oil inlet and outlet of proportional control valve group 4 is connected to first hydraulic fluid port of variable pump 2 and the variable piston rod of variable pump 2 respectively, thereby forms the negative feedback channel of described variable pump 2; Proportional control valve group 4 has adjustable ratio (pressure) setting value, when the oil liquid pressure of the first hydraulic fluid port A of variable pump 2 reaches this setting value, proportional control valve group 4 is opened, the fluid of the first hydraulic fluid port A acts on the variable piston rod of variable pump 2 through proportional control valve group 4, the swash plate angle of variable pump 2 is diminished, and then the discharge capacity of variable pump 2 is reduced, when the oil liquid pressure of the first hydraulic fluid port A of variable pump 2 set value less than this, proportional control valve group 4 was closed.
In the specific implementation, first tube rolling device 5 and second tube rolling device, 6 symmetries can be installed on the jib of piling machinery (as continuous wall grab or revolve dig the reaming rig), the first tube rolling device motor 7 drives with second tube rolling device 6 with first tube rolling device 5 respectively with the second tube rolling device motor 8 and is connected, one end of left and right sides main oil pipe is wound in respectively on first tube rolling device 5 and second tube rolling device 5, be connected in equipment downwards behind the carriage on other end pile warp jib top, thereby provide oil inlet passage and drainback passage for equipment; Motor 1 and variable pump 2 are installed on the inside of getting on the bus of piling machinery; Synchronous control valve group 3 and proportional control valve group 4 are installed on roof.In addition, synchronous control valve group 3 can adopt the flow divider-combiner piece to realize.
In the course of the work, can control the setting value of proportional control valve group 4, for example can make this setting value and main oil pipe transfer the proportional synchronous increase of the degree of depth or minimizing.When promoting, the first hydraulic fluid port A of variable pump 2 proposes the hydraulic fluid port oil-feed on the tube rolling device motor, the following fuel outlet of tube rolling device motor is to the second hydraulic fluid port B oil return of variable pump 2, if the receipts pipe speed of tube rolling device is greater than the hoisting velocity of equipment, main oil pipe will be pulled to hypercompact state, at this moment, system pressure (being the pressure of variable pump 2 first hydraulic fluid ports) reaches the setting value of proportional control valve group 4, proportional control valve group 4 is opened, the fluid of variable pump first hydraulic fluid port is with the variable piston rod of passing ratio control valve group effect to variable pump 2, the variable pump delivery reduces, the receipts pipe speed of tube rolling device slows down, and main oil pipe is fluffed by hypercompact state and is the corresponding rate of tension of the setting value of proportional control valve group 4; If the receipts pipe speed of tube rolling device is lower than the hoisting velocity of equipment, main oil pipe will be in relaxed state, at this moment, system pressure is less than the setting value of proportional control valve group 4, proportional control valve group 4 is closed, and feedback effect is not to the variable piston rod for the fluid of variable pump 2 first hydraulic fluid ports, and the discharge capacity of variable pump 2 increases, tube rolling device is received pipe fast, reaches the rate of tension of the setting value correspondence of proportional control valve group until main oil pipe; In the specific implementation, by given corresponding setting value, can make the self gravitation of the tensile force of main oil pipe when any degree of depth at this depth location the time.When transferring, main oil pipe is being dragged tube rolling device downwards and is being made its reverse rotation, the following fuel outlet of tube rolling device motor is the oil-feed state, carrying hydraulic fluid port on the tube rolling device motor is the oil return state, if the tensile force of main oil pipe is bigger, that the oil liquid pressure that causes variable pump 2 first hydraulic fluid ports is excessive and surpass the setting value of proportional control valve group 4, at this moment, its effect of negative feedback channel, the discharge capacity of variable pump 2 reduces, and main oil pipe is fluffed by hypercompact state be the corresponding rate of tension of the setting value of proportional control valve group 4.
From as can be known above-mentioned, the tube rolling device hydraulic system of the utility model above-described embodiment can change the size of the tensile force that main oil pipe bears, the tensile force that main oil pipe the is born degree of depth residing with it adapts, namely avoided main oil pipe all bearing maximum tensile force in any degree of depth, improve the application life of main oil pipe, thereby reduced construction cost; In addition, owing to adopt enclosed variable pump and two tube rolling device motors to form closed hydraulic loop, compared with prior art, avoid the heat producing losses of system's overflow, improved system effectiveness.
For the core of clearer displaying above-described embodiment, provide a kind of preferred embodiment of above-mentioned enforcement below in conjunction with Fig. 2.In addition, for convenience of explanation, omitted synchronous control valve group 3 among Fig. 2.
In conjunction with shown in Figure 2, in the preferred embodiment, variable pump 2 adopts the A4VG pump, and proportional control valve group 4 adopts ratio sequence valve group 9.
Particularly, ratio sequence valve group 9 preferably includes sequence valve 11 and first overflow valve 14; Sequence valve 11 is hydraulically-controlled type 2/2-way valve, first overflow valve 14 is proportion magnetic valve, the oil-in of sequence valve 11 is connected to the first hydraulic fluid port A of variable pump 2, the oil-out of sequence valve 11 is connected to the right chamber of variable piston rod by the X4 mouth of variable pump 2, first hydraulic control of sequence valve 11 is terminated at the oil-in of sequence valve 11, second hydraulic control of sequence valve 11 is terminated at the oil-in of sequence valve 11 and first overflow valve 14, and the overfall of first overflow valve 14 is connected to fuel tank; In use, by the control electric current (electric current of electromagnetic coil) that changes first overflow valve 14, get final product the setting value of control ratio sequence valve group 9.More preferably, oil circuit between first hydraulic fluid port of ratio sequence valve group 9 and variable pump 2 is provided with reversal valve 18 and/or first throttle valve 17, state by control reversal valve 18, can determine whether enable negative feedback channel, and first throttle valve 17 can avoid the fluid of the first hydraulic fluid port A to impact because of the excessive Comparative Examples control valve of pressure group 9.On the basis of above-mentioned two kinds of preferred situation, ratio sequence valve group 9 also preferably includes second choke valve 12 and the 3rd choke valve 13; The oil-in of sequence valve 11 and the second hydraulic control end are connected to the oil-in of first overflow valve 14 respectively by second choke valve 12 and the 3rd choke valve 13.On the basis of above-mentioned three kinds of preferred situation, the oil-in that ratio sequence valve group 9 also preferably includes second overflow valve, 15, the second overflow valves 15 is connected to the oil-out of sequence valve 11, and the overfall of second overflow valve 15 is connected to fuel tank.On the basis of above-mentioned four kinds of preferred situation, ratio sequence valve group 9 also preferably includes the 4th choke valve 16, the four choke valves 16 and is arranged at the oil-out of sequence valve 11 to the oil circuit between the described variable piston rod.Being provided with of various choke valves helps the control that reduces hydraulic shock power and make hydraulic system more steadily, accurately.
Need to prove that in the above-mentioned optimal way, ratio sequence valve group 9 adopts as above form, but is not limited thereto, in other embodiments, all can adopt as long as can realize the ratio sequence valve group of above-mentioned functions.
Need to prove that in the above-mentioned optimal way, proportional control valve group 4 adopts ratio sequence valve group 9, but be not limited thereto, in other embodiments, all can adopt as long as can realize the proportional control valve of above-mentioned functions, for example, this proportional control valve group 4 can also be the proportional reversing valve group.
Need to prove, in the above-mentioned embodiment, variable pump 2 is the enclosed variable pump, and whole system adopts closed type hydraulic system, but in other embodiments, also can adopt the beginning hydraulic system, in this case, the oil-in of variable pump is connected to fuel tank, the oil-out of variable pump (first hydraulic fluid port) (passes through main reversing valve, flow divider-combiner etc.) be connected to the first tube rolling device motor 7 and the second tube rolling device motor 8 on carry hydraulic fluid port, the following fuel outlet of the first tube rolling device motor 7 and the second tube rolling device motor 8 (passes through flow divider-combiner, main reversing valve etc.) be connected to fuel tank, so also can realize corresponding function of the present utility model.
The utility model embodiment also provides a kind of piling machinery, for example revolve and dig reaming rig or continuous wall grab, this piling machinery is provided with the described tube rolling device hydraulic system of above-described embodiment, because above-mentioned tube rolling device hydraulic system has above-mentioned technique effect, therefore, this piling machinery also should possess corresponding technique effect, and the specific implementation process of its appropriate section is similar to the above embodiments, the specific implementation process of other parts can not given unnecessary details now referring to the associated description of prior art.
The above only is preferred embodiment of the present utility model; not in order to limit the utility model; all within spirit of the present utility model and principle, any modification of doing, be equal to replacement, improvement etc., all should be included within the protection domain of the present utility model.
Claims (10)
1. tube rolling device hydraulic system is characterized in that:
Comprise variable pump (2), proportional control valve group (4) and tube rolling device motor;
First hydraulic fluid port of described variable pump (2) be connected to described tube rolling device motor on carry hydraulic fluid port;
The oil inlet and outlet of described proportional control valve group (4) is connected to first hydraulic fluid port of described variable pump (2) and the variable piston rod of described variable pump (2) respectively, forms the negative feedback channel of described variable pump (2);
The fluid of first hydraulic fluid port of described variable pump (2) acts on described variable piston rod through described proportional control valve group (4) when its pressure reaches the setting value of described proportional control valve group (4).
2. tube rolling device hydraulic system as claimed in claim 1, it is characterized in that: described variable pump (2) is the enclosed variable pump, first hydraulic fluid port of described variable pump (2) be connected to described tube rolling device motor on carry hydraulic fluid port, second hydraulic fluid port of described variable pump (2) is connected to the following fuel outlet of described tube rolling device motor.
3. tube rolling device hydraulic system as claimed in claim 2, it is characterized in that: described tube rolling device motor comprises the first tube rolling device motor (7) and the second tube rolling device motor (8); Described tube rolling device hydraulic system also comprises synchronous control valve group (3); First hydraulic fluid port of described variable pump (2) by described synchronous control valve group (3) be connected to the described first tube rolling device motor (7) and the described second tube rolling device motor (8) on carry hydraulic fluid port, second hydraulic fluid port of described variable pump (2) is connected to the following fuel outlet of the described first tube rolling device motor (7) and the described second tube rolling device motor (8) by described synchronous control valve group (3).
4. tube rolling device hydraulic system as claimed in claim 1, it is characterized in that: the oil circuit between first hydraulic fluid port of described proportional control valve group (4) and described variable pump (2) is provided with reversal valve (18) and/or first throttle valve (17).
5. as each described tube rolling device hydraulic system of claim 1 to 4, it is characterized in that: described proportional control valve group (4) is ratio sequence valve group (9) or proportional reversing valve group.
6. tube rolling device hydraulic system as claimed in claim 5, it is characterized in that: described ratio sequence valve group (9) comprises sequence valve (11) and first overflow valve (14); Described sequence valve (11) is hydraulically-controlled type, and described first overflow valve (14) is proportion magnetic valve; The oil-in of described sequence valve (11) is connected to first hydraulic fluid port of described variable pump (2), the oil-out of described sequence valve (11) is connected to the variable piston rod of described variable pump (2), first hydraulic control of described sequence valve (11) is terminated at the oil-in of described sequence valve (11), the second hydraulic control end of described sequence valve (11) is connected to the oil-in of described sequence valve (11) and the oil-in of described first overflow valve (14) simultaneously, and the overfall of described first overflow valve (14) is connected to fuel tank.
7. tube rolling device hydraulic system as claimed in claim 6, it is characterized in that: described ratio sequence valve group (9) also comprises second choke valve (12) and the 3rd choke valve (13); The oil-in of described sequence valve (11) and the second hydraulic control end are connected to the oil-in of described first overflow valve (14) respectively by described first throttle valve (12) and described second choke valve (13).
8. tube rolling device hydraulic system as claimed in claim 6, it is characterized in that: described ratio sequence valve group (9) also comprises second overflow valve (15), the oil-in of described second overflow valve (15) is connected to the oil-out of described sequence valve (11), and the overfall of described second overflow valve (15) is connected to fuel tank.
9. tube rolling device hydraulic system as claimed in claim 6, it is characterized in that: described ratio sequence valve group (9) also comprises the 4th choke valve (16), and described the 4th choke valve (16) is arranged at the oil-out of described sequence valve (11) to the oil circuit between the described variable piston rod.
10. piling machinery, it is characterized in that: described piling machinery is provided with each described tube rolling device hydraulic system of claim 1 to 9.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220739246 CN203066069U (en) | 2012-12-28 | 2012-12-28 | Pipe winding device hydraulic system and piling machinery |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220739246 CN203066069U (en) | 2012-12-28 | 2012-12-28 | Pipe winding device hydraulic system and piling machinery |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN203066069U true CN203066069U (en) | 2013-07-17 |
Family
ID=48764880
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201220739246 Withdrawn - After Issue CN203066069U (en) | 2012-12-28 | 2012-12-28 | Pipe winding device hydraulic system and piling machinery |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN203066069U (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103062142A (en) * | 2012-12-28 | 2013-04-24 | 三一重工股份有限公司 | Pipe reeling device hydraulic system and piling machine |
| CN104019064A (en) * | 2014-06-03 | 2014-09-03 | 三一汽车制造有限公司 | Closed pump hydraulic system, closed pump and engineering machinery |
-
2012
- 2012-12-28 CN CN 201220739246 patent/CN203066069U/en not_active Withdrawn - After Issue
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103062142A (en) * | 2012-12-28 | 2013-04-24 | 三一重工股份有限公司 | Pipe reeling device hydraulic system and piling machine |
| CN103062142B (en) * | 2012-12-28 | 2015-12-23 | 三一重工股份有限公司 | Tube rolling device hydraulic system and piling machinery |
| CN104019064A (en) * | 2014-06-03 | 2014-09-03 | 三一汽车制造有限公司 | Closed pump hydraulic system, closed pump and engineering machinery |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20130717 Effective date of abandoning: 20151223 |
|
| C25 | Abandonment of patent right or utility model to avoid double patenting |