CN201306256Y - Axial plunger variable pump - Google Patents
Axial plunger variable pump Download PDFInfo
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- CN201306256Y CN201306256Y CNU2008201383754U CN200820138375U CN201306256Y CN 201306256 Y CN201306256 Y CN 201306256Y CN U2008201383754 U CNU2008201383754 U CN U2008201383754U CN 200820138375 U CN200820138375 U CN 200820138375U CN 201306256 Y CN201306256 Y CN 201306256Y
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- pressure
- oil
- amplifier
- comparator
- unsteady state
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Abstract
The utility model relates to an axial plunger variable pump which comprises an inclined disc, a sliding shoe, a plunger, a plunger cylinder body and an oil distributing disc, wherein, the front inclined part and the rear inclined part of the inclined disc are respectively connected with a push rod of a push oil cylinder; cavities of the two push oil cylinder are respectively communicated with two output openings of a unsteady valve which is controlled by a controller; the controller comprises a first comparator, an amplifier and a threshold command source, wherein the amplifier is connected with a second amplifier. The utility model can sense the accurate change of the displacement of the variable pump, quickly control the angles of the inclined disc, and have the advantages of little energy consumption and high efficiency.
Description
Technical field
The utility model relates to a kind of variable displacement pump, especially a kind of axial plunger type variable capacity pump.
Background technique
Axial plunger type variable capacity pump, because that it has a volume is little, in light weight, specific power is big, is easy to advantages such as control, is widely used at present in the various hydraulic systems.
Traditional axial plunger type variable capacity pump is made up of variable displacement pump that has the inclination swash plate and variable controlling mechanism, its controlling mechanism comprises proportional pressure valve, proportional flow control valve and is installed in return spring on the swash plate, when the pressure at the oil drain out place of variable displacement pump during less than pressure threshold, the pressure reduction that proportional pressure valve, proportional flow control valve produce to system's delivery pressure flow by setting value, stream difference increase, promote swash plate and beat fast tiltedly, increase discharge capacity.When the pressure at the oil drain out place of variable displacement pump during greater than pressure threshold, the automatic draining of oil drain valve on the variable displacement pump, reduce the actual pressure at oil drain out place, proportional pressure valve, proportional flow control valve reduce by pressure reduction, the stream difference of setting value to system's delivery pressure flow generation simultaneously, swash plate is set upright under the effect of return spring gradually, thereby the energy output of realization hydraulic system is followed the variation of load state and changed.But because the active force of return spring is little, it is slow to make swash plate set upright speed; Reduce the actual pressure of oil drain out by oil drain valve nature draining, and the lag period is grown, existed to the reaction time of proportional pressure valve, proportional flow control valve, and can not realize digital control, cause traditional axial plunger type variable capacity pump to have the accurately displacement variation of perception variable displacement pump, shortcomings such as return speed is slow, and energy consumption is big, efficient is low.
Summary of the invention
The utility model has proposed a kind of accurately variation of perception variable displacement pump discharge capacity in time at above-mentioned shortcoming, controls the swash plate angle quickly and accurately, consuming little energy, the axial plunger type variable capacity pump that efficient is high.
Axial plunger type variable capacity pump described in the utility model comprises:
Be articulated in swash plate on the swash plate seat in the mode that can change the relative tilt angle;
Rotating plunger cylinder along the circumferential direction is furnished with axial plunger hole in the described cylinder body; Described plunger hole front portion is provided with plunger, and the front end of described plunger connects the piston shoes that can slide against described swash plate face in the ball pivot mode;
The rear portion of described plunger cylinder connects one fen food tray, on the described minute food tray inlet port and oil drain out is arranged, and described inlet port and oil drain out dock the rear portion of described plunger hole; Described inlet port and oil drain out all are connected with transport pipe;
It is characterized in that:
The portion that leans forward of described swash plate and layback portion are connected the push rod of a push action cylinder respectively, and described two push action cylinders form the arm of force pair at the tilt angle that changes described swash plate;
The inner chamber of described two push action cylinders is communicated with two delivery outlets of a unsteady state valve respectively; Described unsteady state valve is controlled by a controller;
Described controller comprises first comparator, amplifier, threshold command source, the positive-negative input end of described first comparator connects described threshold command source and respectively and measures the displacement transducer of the tilt displacement of described swash plate, the flow threshold that the output of described threshold command source is set according to user's needs, the described displacement transducer output displacement signal corresponding with actual flow, the comparative result of described first comparator output flow threshold value and actual flow; The positive input terminal of described amplifier connects described first comparator, and the output terminal of described amplifier connects described unsteady state valve, and the output signal of amplifier is controlled the signal that described unsteady state valve distributes the oil pump capacity of two delivery outlets.
In order to ensure giving the steady fuel feeding of load constant voltage, the high successively order of magnitude of the data processing speed of the velocity inertial of described swash plate, the regulation and control speed of described unsteady state valve, the induction speed of described pressure transducer, described controller.
Further, the pressure transducer of measuring oil extraction pressure is housed on the described oil drain out; The negative input end of described amplifier connects second comparator, the positive-negative input end of described second comparator connects described threshold command source and described pressure transducer respectively, the pressure threshold that the output of described threshold command source is set according to user's needs, the actual pressure of described pressure transducer output oil drain out, the comparative result of described second comparator delivery pressure threshold value and actual pressure.
Further, be provided with mode selection module in the described controller, mode selection module control amplifier selection pressure pattern or flow rate mode or flow rate pressure pattern control unsteady state valve;
When amplifier selection pressure pattern, amplifier is only carried out following operation with reference to the result of described second comparator output:
When (1) actual pressure is less than pressure threshold, amplifier output signal makes that the hydraulic fluid port A oil-feed that is connected with the oil cylinder C that is connected swash plate layback portion in the unsteady state valve is big, another hydraulic fluid port B oil-feed is little, the piston forward of oil cylinder C is advanced, the piston of another oil cylinder D draws back, swashplate angle increases, and pump delivery increases, oil drain out pressure increases;
When (2) actual pressure is greater than pressure threshold, amplifier output signal makes that the hydraulic fluid port A oil-feed of unsteady state valve is little, hydraulic fluid port B oil-feed is big, the push rod that makes the push rod that is connected on the oil cylinder C draw back, be connected on the oil cylinder D marches forward, and swashplate angle reduces, and pump delivery reduces, oil drain out pressure reduces.
When amplifier was selected flow rate mode, amplifier was only carried out following operation with reference to the result of described first comparator output:
When (1) actual flow is less than flow threshold, amplifier output signal makes in the unsteady state valve that hydraulic fluid port A oil-feed is big, another hydraulic fluid port B oil-feed is little, the piston forward of oil cylinder C is advanced, the piston of another oil cylinder D draws back, swashplate angle increases, pump delivery increases, oil drain out pressure increases;
When (2) actual flow is greater than flow threshold, amplifier output signal makes that the hydraulic fluid port A oil-feed of unsteady state valve is little, hydraulic fluid port B oil-feed is big, the push rod that makes the push rod that is connected on the oil cylinder C draw back, be connected on the oil cylinder D marches forward, and swashplate angle reduces, and pump delivery reduces, oil drain out pressure reduces.
When amplifier was selected the flow rate pressure pattern, amplifier was carried out following operation with reference to the result of described first comparator output and the result of described second comparator output simultaneously:
(1) result according to described first comparator output judges that whether actual flow is greater than flow threshold;
When (2) actual flow is greater than flow threshold, amplifier output signal makes that the hydraulic fluid port A oil-feed of unsteady state valve is little, hydraulic fluid port B oil-feed is big, the push rod that makes the push rod that is connected on the oil cylinder C draw back, be connected on the oil cylinder D marches forward, and swashplate angle reduces, and pump delivery reduces, oil drain out pressure reduces;
When (3) actual flow is less than flow threshold, judge that according to the pressure threshold of described second comparator output and the comparative result of actual pressure whether actual pressure is greater than pressure threshold;
When (4) actual pressure is greater than pressure threshold, amplifier output signal makes that the hydraulic fluid port A oil-feed of unsteady state valve is little, hydraulic fluid port B oil-feed is big, the push rod that makes the push rod that is connected on the oil cylinder C draw back, be connected on the oil cylinder D marches forward, and swashplate angle reduces, and pump delivery reduces, oil drain out pressure reduces;
When (5) actual pressure is less than pressure threshold, amplifier output signal makes in the unsteady state valve that hydraulic fluid port A oil-feed is big, another hydraulic fluid port B oil-feed is little, the piston forward of oil cylinder C is advanced, the piston of another oil cylinder D draws back, swashplate angle increases, pump delivery increases, oil drain out pressure increases.
Further again, described unsteady state valve is differential pressure type unsteady state valve or slide column type unsteady state valve.
Control principle of the present utility model:
During original state, the pressure of oil drain out is zero, swash plate is vertical with transmission shaft, actual pressure less than pressure threshold, actual flow less than pressure threshold, flow; Open system, hydraulic fluid port A oil-feed is big in the amplifier output signal control unsteady state valve, another hydraulic fluid port B oil-feed is little, the piston forward of oil cylinder C is advanced, the piston of another oil cylinder D draws back, swashplate angle increases, actual flow increases, pump delivery increases, the actual pressure of oil drain out increases, and actual flow constantly approaches flow threshold, actual pressure and constantly approaches pressure threshold.
When the load of oil drain out connection increased with oil mass, the actual pressure that described pressure transducer is sensed reduced; Hydraulic fluid port A oil-feed is big in the amplifier output signal control unsteady state valve, another hydraulic fluid port B oil-feed is little, the piston forward of oil cylinder C is advanced, the piston of another oil cylinder D draws back, swashplate angle increases, and actual flow increases, pump delivery increases, the actual pressure of oil drain out increases; If actual pressure is all the time less than pressure threshold, under the pressure pattern, swashplate angle constantly increases the limit position until the swash plate inclination; Under the flow rate pressure pattern, when actual flow is no more than flow threshold, swashplate angle constantly increases, pump delivery increases the actual flow increase, the oil drain out actual pressure increases, but when actual flow surpasses when reaching flow threshold, hydraulic fluid port A oil-feed reduces in the amplifier output signal control unsteady state valve, another hydraulic fluid port B oil-feed increases, the piston of oil cylinder C is drawn back, the piston forward of another oil cylinder D advances, swashplate angle reduces, actual flow reduces.
When the load of oil drain out connection reduced with oil mass, the actual pressure that described pressure transducer is sensed increased; Amplifier output signal makes that the hydraulic fluid port A oil-feed of unsteady state valve is little, hydraulic fluid port B oil-feed is big, and the push rod that makes the push rod that is connected on the oil cylinder C draw back, be connected on the oil cylinder D marches forward, and swashplate angle reduces, and pump delivery reduces, oil drain out pressure reduces.
When the variable displacement pump end-of-job, shutdown system, hydraulic fluid port A oil-feed is little in the amplifier output signal control unsteady state valve, another hydraulic fluid port B oil-feed is big, the piston of oil cylinder C is drawn back, the piston forward of another oil cylinder D advances, swashplate angle is reduced to zero, and actual flow is reduced to, and actual pressure zero, oil drain out is reduced to zero.
Here, we are noted that systematically regulation process is not one-time-reach-place, but continuous adaptive is regulated the process that intelligence is approached.Because each regulation and control, actual flow and actual pressure all can change, and the output signal of first comparator and second comparator has also just changed, and the swashplate angle in next regulation and control cycle of swash plate has also just changed.Therefore, swash plate is constantly motion, is one and constantly adjusts swashplate angle to adapt to the continuous regulation process of discharge capacity and variation in pressure.The utility model is by the motion of unsteady state valve control oil cylinder, system can per second nearly thousand times speed regulate and control, the discharge capacity of pump delivery and load request is adapted.The utility model adopts unique regulation and control theory, can continue fuel feeding reposefully for load.
The utility model has the advantages that: can regulate the position of swash plate intelligently according to the needs of changes in flow rate, its force mechanism is reasonable, reaction velocity fast, it is little to regulate rapidly and accurately, consume energy.
Description of drawings
Fig. 1 is a schematic representation of the present utility model;
Fig. 2 has only the main flow chart under the situation of a comparator for the utility model;
Fig. 3 has the main flow chart of the situation down-off-pressure pattern of two comparators for the utility model.
Embodiment:
Embodiment one
With reference to Fig. 1, Fig. 2:
Axial plunger type variable capacity pump described in the utility model comprises:
Be articulated in swash plate 1 on the swash plate seat in the mode that can change the relative tilt angle;
Rotating plunger cylinder 2 along the circumferential direction is furnished with axial plunger hole 21 in the described cylinder body 2; Described plunger hole 21 front portions are provided with plunger 22, and the front end of described plunger 22 connects the piston shoes 11 that can slide against described swash plate 1 face in the ball pivot mode;
The rear portion of described plunger cylinder 2 connects one fen food tray 3, and inlet port 31 and oil drain out 32 are arranged on the described minute food tray 3, the rear portion of described inlet port 31 and the described plunger hole 21 of oil drain out 32 butt joints; Described inlet port 31 and oil drain out 32 all are connected with transport pipe 33;
The portion that leans forward 13 of described swash plate 1 connects push action cylinder 4D by push rod 41, and the layback portion 12 of described swash plate 1 connects push action cylinder 4C by push rod 41, and described two push action cylinders form the arm of force pair at the tilt angle that changes described swash plate 1;
The inner chamber of described two push action cylinders is communicated with two delivery outlet 5A of a unsteady state valve 5,5B respectively; Described unsteady state valve 5 is controlled by a controller;
Described controller comprises first comparator 61, amplifier 63, threshold command source 64, the positive-negative input end of described first comparator 61 connects described threshold command source 64 and respectively and measures the displacement transducer 8 of the tilt displacement of described swash plate, the flow threshold that 64 outputs of described threshold command source are set according to user's needs, the described displacement transducer 8 outputs displacement signal corresponding with actual flow, the comparative result of described first comparator, 61 output flow threshold values and actual flow; The positive input terminal of described amplifier 63 connects described first comparator 61, and the output terminal of described amplifier 63 connects described unsteady state valve 5, and the output signal of amplifier 61 is controlled two delivery outlet 5A of described unsteady state valve 5, the signal of the oil pump capacity of 5B.
In order to ensure giving the steady fuel feeding of load constant voltage, the high successively order of magnitude of the data processing speed of the regulation and control speed of the velocity inertial of described swash plate 1, described unsteady state valve 5, the induction speed of described pressure transducer 7, described controller.
When (1) actual flow is less than flow threshold, amplifier 63 output signals make that the hydraulic fluid port 5A oil-feed that is connected with the oil cylinder 4D that is connected swash plate 1 layback portion 12 in the unsteady state valve 5 is big, another hydraulic fluid port 5B oil-feed is little, the piston forward of oil cylinder 4D is advanced, the piston of another oil cylinder 4C draws back, swash plate 1 inclination angle increases, and pump delivery increases, oil drain out pressure increases;
When (2) actual flow is greater than flow threshold, amplifier 63 output signals make that the hydraulic fluid port 5A oil-feed of unsteady state valve 5 is little, hydraulic fluid port 5B oil-feed is big, the push rod 41 that makes the push rod 41 that is connected on the oil cylinder 4D draw back, be connected on the oil cylinder 4C marches forward, swashplate angle reduces, and pump delivery reduces, oil drain out pressure reduces.
Control principle of the present utility model:
During original state, the pressure of oil drain out 32 is zero, swash plate 1 is vertical with transmission shaft, actual pressure less than pressure threshold less than pressure threshold; Open system, hydraulic fluid port 5A oil-feed is big in the amplifier 63 output signals control unsteady state valve 5, another hydraulic fluid port 5B oil-feed is little, the piston forward of oil cylinder 4D is advanced, the piston of another oil cylinder 4C draws back, swash plate 1 inclination angle increases, actual flow increases, pump delivery increases, the actual pressure of oil drain out increases, and actual flow constantly approaches flow threshold, actual pressure and constantly approaches pressure threshold.
When the variable displacement pump end-of-job, shutdown system, hydraulic fluid port 5A oil-feed is little in the amplifier 63 output signals control unsteady state valve 5, another hydraulic fluid port 5B oil-feed is big, the piston of oil cylinder 4D is drawn back, the piston forward of another oil cylinder 4C advances, swashplate angle is reduced to zero, and actual flow is reduced to, and actual pressure zero, oil drain out is reduced to zero.
Embodiment two
Referring to Fig. 1, Fig. 3;
Embodiment two is with embodiment one difference part:
The pressure transducer 7 of measuring oil extraction pressure is housed on the described oil drain out 32;
The negative input end of described amplifier 63 connects second comparator 62, the positive-negative input end of described second comparator 62 connects described threshold command source 64 and described pressure transducer 7 respectively, the pressure threshold that 64 outputs of described threshold command source are set according to user's needs, the actual pressure of described pressure transducer 7 output oil drain outs 32, the comparative result of described second comparator, 62 delivery pressure threshold values and actual pressure.
Be provided with mode selection module in the described controller, mode selection module control amplifier 63 selection pressure patterns or flow rate mode or flow rate pressure pattern control unsteady state valve;
(1) result according to 61 outputs of described first comparator judges that whether actual flow is greater than flow threshold;
When (2) actual flow is greater than flow threshold, amplifier 63 output signals make that the hydraulic fluid port 5A oil-feed of unsteady state valve 5 is little, hydraulic fluid port 5B oil-feed is big, the push rod that makes the push rod that is connected on the oil cylinder 4C draw back, be connected on the oil cylinder 4D marches forward, swashplate angle reduces, and pump delivery reduces, oil drain out pressure reduces;
When (3) actual flow was less than flow threshold, the result who exports according to described second comparator 62 judged that whether actual pressure is greater than pressure threshold;
When (4) actual pressure is greater than pressure threshold, amplifier 63 output signals make that the hydraulic fluid port 5A oil-feed of unsteady state valve 5 is little, hydraulic fluid port 5B oil-feed is big, the push rod 41 that makes the push rod 41 that is connected on the oil cylinder 4C draw back, be connected on the oil cylinder 4D marches forward, swashplate angle reduces, and pump delivery reduces, oil drain out pressure reduces;
When (5) actual pressure is less than pressure threshold, amplifier 63 output signals make in the unsteady state valve 5 that hydraulic fluid port 5A oil-feed is big, another hydraulic fluid port 5B oil-feed is little, the piston forward of oil cylinder 4C is advanced, the piston of another oil cylinder 4D draws back, swashplate angle increases, pump delivery increases, oil drain out pressure increases.
Embodiment two is with the difference of embodiment one control principle:
When the load of oil drain out 32 connections increased with oil mass, the actual pressure that described pressure transducer 7 is sensed reduced; Hydraulic fluid port 5A oil-feed is big in the amplifier 63 output signals control unsteady state valve 5, another hydraulic fluid port 5B oil-feed is little, the piston forward of oil cylinder 4C is advanced, the piston of another oil cylinder 4D draws back, swashplate angle increases, and actual flow increases, pump delivery increases, the actual pressure of oil drain out increases; If actual pressure is all the time less than pressure threshold, when actual flow is no more than flow threshold, swashplate angle constantly increases, pump delivery increases the actual flow increase, the oil drain out actual pressure increases, but when actual flow surpasses when reaching flow threshold, hydraulic fluid port 5A oil-feed reduces in the amplifier 63 output signals control unsteady state valve 5, another hydraulic fluid port 5B oil-feed increases, the piston of oil cylinder 4C is drawn back, the piston forward of another oil cylinder 4D advances, swashplate angle reduces, actual flow reduces.
All right selection pressure pattern in the present embodiment, when selecting pressure pattern, only with reference to second comparator, 62 control unsteady state valves 5, only the result of described second comparator of reference 63 outputs carries out following operation to amplifier 63:
Actual pressure is during less than pressure threshold, amplifier output signal makes that the hydraulic fluid port A oil-feed that is connected with the oil cylinder C that is connected swash plate layback portion in the unsteady state valve is big, another hydraulic fluid port B oil-feed is little, the piston forward of oil cylinder C is advanced, the piston of another oil cylinder D draws back, swashplate angle increases, and pump delivery increases, oil drain out pressure increases;
Actual pressure is during greater than pressure threshold, amplifier output signal makes that the hydraulic fluid port A oil-feed of unsteady state valve is little, hydraulic fluid port B oil-feed is big, the push rod that makes the push rod that is connected on the oil cylinder C draw back, be connected on the oil cylinder D marches forward, and swashplate angle reduces, and pump delivery reduces, oil drain out pressure reduces.
When selecting flow rate mode, only with reference to first comparator, 61 control unsteady state valves 5, the control mode of this moment is identical with embodiment one for amplifier 63.
The described content of this specification embodiment only is enumerating the way of realization of inventive concept; protection domain of the present utility model should not be regarded as only limiting to the concrete form that embodiment states, protection domain of the present utility model also reach in those skilled in the art according to the utility model design the equivalent technologies means that can expect.
Claims (4)
1, axial plunger type variable capacity pump described in the utility model comprises:
Be articulated in swash plate on the swash plate seat in the mode that can change the relative tilt angle;
Rotating plunger cylinder along the circumferential direction is furnished with axial plunger hole in the described cylinder body; Described plunger hole front portion is provided with plunger, and the front end of described plunger connects the piston shoes that can slide against described swash plate face in the ball pivot mode;
The rear portion of described plunger cylinder connects one fen food tray, on the described minute food tray inlet port and oil drain out is arranged, and described inlet port and oil drain out dock the rear portion of described plunger hole; Described inlet port and oil drain out all are connected with transport pipe;
It is characterized in that:
The portion that leans forward of described swash plate and layback portion are connected the push rod of a push action cylinder respectively, and described two push action cylinders form the arm of force pair at the tilt angle that changes described swash plate;
The inner chamber of described two push action cylinders is communicated with two delivery outlets of a unsteady state valve respectively; Described unsteady state valve is controlled by a controller;
Described controller comprises first comparator, amplifier, threshold command source, and the positive-negative input end of described first comparator connects described threshold command source and respectively and measures the displacement transducer of the tilt displacement of described swash plate; The positive input terminal of described amplifier connects described first comparator, and the output terminal of described amplifier connects described unsteady state valve.
2, axial plunger type variable capacity pump as claimed in claim 1 is characterized in that: the pressure transducer of measuring oil extraction pressure is housed on the described oil drain out; The negative input end of described amplifier connects second comparator, the positive-negative input end of described second comparator connects described threshold command source and described pressure transducer respectively, the pressure threshold that the output of described threshold command source is set according to user's needs, the actual pressure of described pressure transducer output oil drain out, the comparative result of described second comparator delivery pressure threshold value and actual pressure.
3, axial plunger type variable capacity pump as claimed in claim 2 is characterized in that: be provided with mode selection module in the described controller, mode selection module control amplifier selection pressure pattern or flow rate mode or flow rate pressure pattern control unsteady state valve.
4, as the described axial plunger type variable capacity pump of one of claim 1 to 3, it is characterized in that: described unsteady state valve is differential pressure type unsteady state valve or slide column type unsteady state valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008201383754U CN201306256Y (en) | 2008-09-18 | 2008-09-18 | Axial plunger variable pump |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CNU2008201383754U CN201306256Y (en) | 2008-09-18 | 2008-09-18 | Axial plunger variable pump |
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| Publication Number | Publication Date |
|---|---|
| CN201306256Y true CN201306256Y (en) | 2009-09-09 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNU2008201383754U Expired - Fee Related CN201306256Y (en) | 2008-09-18 | 2008-09-18 | Axial plunger variable pump |
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| CN (1) | CN201306256Y (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103696956A (en) * | 2013-12-06 | 2014-04-02 | 北京工业大学 | Torque-balanced flow distribution pair for water hydraulic axial piston pumps |
| CN106894961A (en) * | 2015-12-17 | 2017-06-27 | 熵零技术逻辑工程院集团股份有限公司 | A kind of hydraulic mechanism |
-
2008
- 2008-09-18 CN CNU2008201383754U patent/CN201306256Y/en not_active Expired - Fee Related
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103696956A (en) * | 2013-12-06 | 2014-04-02 | 北京工业大学 | Torque-balanced flow distribution pair for water hydraulic axial piston pumps |
| CN103696956B (en) * | 2013-12-06 | 2016-04-06 | 北京工业大学 | A kind of water hydraulic axial piston pump Port Plate Pair of equalising torque |
| CN106894961A (en) * | 2015-12-17 | 2017-06-27 | 熵零技术逻辑工程院集团股份有限公司 | A kind of hydraulic mechanism |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20090909 Termination date: 20140918 |
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| EXPY | Termination of patent right or utility model |