CN101940092B - Two-degree-of-freedom single hinged profiling mechanism - Google Patents

Two-degree-of-freedom single hinged profiling mechanism Download PDF

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Publication number
CN101940092B
CN101940092B CN2010102353739A CN201010235373A CN101940092B CN 101940092 B CN101940092 B CN 101940092B CN 2010102353739 A CN2010102353739 A CN 2010102353739A CN 201010235373 A CN201010235373 A CN 201010235373A CN 101940092 B CN101940092 B CN 101940092B
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China
Prior art keywords
liquid accumulator
gas
profiling
oil
pressure relief
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Expired - Fee Related
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CN2010102353739A
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CN101940092A (en
Inventor
贾洪雷
李广宇
王蔚
徐峰
孙明哲
吴艳丽
谭宏杰
李春胜
黄东岩
张家源
徐勇
王安
孙卓
张丁佟
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Jilin University
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Jilin University
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Publication of CN101940092B publication Critical patent/CN101940092B/en
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Abstract

The invention discloses a two-degree-of-freedom single hinged profiling mechanism, belonging to the technical field of agricultural machinery. In the invention, a single hinged joint and a piston gas-liquid energy accumulator are connected with a profiling part through a hinged front rack, and one end of a piston rod is provided with an upper profiling overtravel-limit switch and a lower profiling overtravel-limit switch for a hydraulic control system; when the profiling part makes profiling motion around the single hinged joint due to external force, the piston rod makes stretching motion, corresponding fore change is generated at the same time, and the force balance of the profiling mechanism is rebuilt; when the profiling quantity is excessive, the hydraulic control system and a serial gas-liquid energy accumulator group are utilized to change the stretching direction of the piston rod, thereby changing the profiling tendency; and the piston rod also can be locked on a fixed position, so that the two-degree-of-freedom mechanism is converted into a rigid triangular mechanism, thereby facilitating the transportation and the transfer of the profiling part. The mechanism solves the problem of unstable operation quality of the traditional single hinged mechanism, has the advantages of compact structure, controllable profiling, convenient adjustment, strong adaptability and high automaticity, can realize remote control, and is beneficial to the design and the exploitation of agricultural machinery products.

Description

The hinged feeler mechanism of double freedom list
Technical field
The invention belongs to agricultural machinery technological field, be specifically related to the hinged feeler mechanism of a kind of double freedom list.
Background technology
Single hinged feeler mechanism is common a kind of feeler mechanism on the agricultural machinery, and it has advantages such as simple in structure, easy for installation, but is difficult for guaranteeing the profiling uniformity of workpiece, is used for seldom using on seeding machinery on the cultivating tillage equipment more.
In recent years, along with the raising of agricultural machinery equipment and the popularization of protective farming technique, various large-scale, constantly appearance of ultra-large type integration of operation agricultural machinery equipment, frame for movement numerous and complicated, operation type variation.But integration of operation facility such as rotary tillage sower, combined soil preparing machine require the compact separated type operation of complete machine, transportation is reliable, profiling property is good.Parallel four connecting rod feeler mechanisms commonly used are simple in structure, but aspect transportation weight capacity and longitudinal size, exist not enough; The employing mechanism that is rigidly connected can guarantee complete machine Transport Safety and strength of parts, if but the operation surface relief is bigger, just can not guarantee the profiling uniformity.
Summary of the invention
The object of the present invention is to provide a kind of compact conformation, the hinged feeler mechanism of good, easy to adjust, the adaptable double freedom list of profiling performance.
The present invention is made up of single pin joint 4, series connection gas-liquid accumulator group, hydraulic pump 12, hydraulic control system and auxiliary hydraulic pressure element; Wherein single pin joint 4 is connected with profiling parts 3 through hinged anterior frame 1 with the piston type gas-liquid accumulator 2 of series connection gas-liquid accumulator group, and piston rod one end of piston type gas-liquid accumulator 2 is equipped with the last profiling travel switch 6 and following profiling travel switch 7 of hydraulic control system; Normally closed type bi-bit bi-pass solenoid directional control valve 15 oil-ins of hydraulic control system are connected with auxiliary gas-liquid accumulator 5 grease chambeies of series connection gas-liquid accumulator group with adjustable throttling I 16a through auxiliary hydraulic pressure element Pressure relief valve I 13a; 3-position-3-way solenoid directional control valve 9 oil-ins of hydraulic control system are connected with piston type gas-liquid accumulator 2 grease chambeies of series connection gas-liquid accumulator group with adjustable throttling II 16b through auxiliary hydraulic pressure element Pressure relief valve II 13b; 3-position 4-way solenoid directional control valve 10 oil-ins of hydraulic control system are connected with hydraulic pump 12 through auxiliary hydraulic pressure element adjustable throttling III16c, Pressure relief valve III13c and check valve III14c; First oil-out is connected with oil cylinder 11; Second oil-out is connected with auxiliary gas-liquid accumulator 5 grease chambeies of series connection gas-liquid accumulator group through the check valve I of auxiliary hydraulic pressure element 14a, Pressure relief valve I 13a and adjustable throttling I 16a, and the 3rd oil-out is connected with piston type gas-liquid accumulator 2 grease chambeies of series connection gas-liquid accumulator group through auxiliary hydraulic pressure element check valve II 14b, Pressure relief valve II 13b and adjustable throttling II16b.
Series connection gas-liquid accumulator group is made up of piston type gas-liquid accumulator 2, auxiliary gas-liquid accumulator 5 and pressurize gas-liquid accumulator 8; Wherein air chamber one end and the anterior frame 1 of piston type gas-liquid accumulator 2 are hinged, and piston rod one end and the profiling parts 3 of piston type gas-liquid accumulator 2 are hinged; Air chamber one end of auxiliary gas-liquid accumulator 5 is connected through the air chamber of pneumatic circuit with piston type gas-liquid accumulator 2, and grease chamber's one end of auxiliary gas-liquid accumulator 5 is connected with hydraulic control system; The air chamber one end sealing of pressurize gas-liquid accumulator 8, grease chamber's one end of pressurize gas-liquid accumulator 8 is connected with grease chamber's one end of piston type gas-liquid accumulator 2 through hydraulic control component.
Hydraulic control system is made up of normally closed type bi-bit bi-pass solenoid directional control valve 15,3-position-3-way solenoid directional control valve 9,3-position 4-way solenoid directional control valve 10, last profiling travel switch 6 and following profiling travel switch 7; Wherein normally closed type bi-bit bi-pass solenoid directional control valve 15 oil-ins are connected with auxiliary gas-liquid accumulator 5 grease chambeies of series connection gas-liquid accumulator group with adjustable throttling I 16a through the Pressure relief valve I of auxiliary hydraulic pressure element 13a, and oil-out is connected with oil cylinder 11; 3-position-3-way solenoid directional control valve 9 oil-ins are connected with the grease chamber of the piston type gas-liquid accumulator 2 of series connection gas-liquid accumulator group with adjustable throttling II 16b through the Pressure relief valve II of auxiliary hydraulic pressure element 13b; First oil-out is connected with oil cylinder 11, the pressurize gas-liquid accumulator 8 of second oil-out and the gas-liquid accumulator group of connecting; 3-position 4-way solenoid directional control valve 10 oil-ins are connected with hydraulic pump 12 through adjustable throttling III16c, Pressure relief valve III13c and the check valve III14c of auxiliary hydraulic pressure element; First oil-out is connected with oil cylinder 11; Second oil-out is connected with auxiliary gas-liquid accumulator 5 grease chambeies of series connection gas-liquid accumulator group through the check valve I of auxiliary hydraulic pressure element 14a, Pressure relief valve I 13a and adjustable throttling I 16a, and the 3rd oil-out is connected with piston type gas-liquid accumulator 2 grease chambeies of series connection gas-liquid accumulator group through the check valve II of auxiliary hydraulic pressure element 14b, Pressure relief valve II 13b and adjustable throttling II 16b; Last profiling travel switch 6 places piston type gas-liquid accumulator 2 piston rods one end with following profiling travel switch 7.
The auxiliary hydraulic pressure element is made up of Pressure relief valve I 13a, Pressure relief valve II 13b, Pressure relief valve III13c, check valve I 14a, check valve II 14b, check valve III14c, adjustable throttling I 16a, adjustable throttling II 16b and adjustable throttling III16c; Wherein Pressure relief valve I 13a places between check valve I 14a and the adjustable throttling I 16a; Pressure relief valve II 13b places between check valve II 14b and the adjustable throttling II 16b, and Pressure relief valve III13c places between check valve III14c and the adjustable throttling III16c.
The course of work of the present invention is following:
1. initialization position
1) before 3 operations of profiling parts, 2DT energising, other switch is in reset mode, and hydraulic pump 12 is grease chamber's fuel feeding of auxiliary gas-liquid accumulator 5, when the grease chamber reaches required volume, the 2DT power-off restoration; 2) A1 of manual adjustments 3-position 4-way solenoid directional control valve 10 or 3DT energising, other switch is in reset mode, and hydraulic pump 12 is grease chamber's fuel feeding of piston type gas-liquid accumulator 2 and pressurize gas-liquid accumulator 8, and piston rod will shorten; 3) A3 of manual adjustments 3-position-3-way solenoid directional control valve 9 or 5DT energising, other switch is in reset mode, and directly to oil cylinder 11 dischargings, piston rod will extend the hydraulic oil of piston type gas-liquid accumulator 2 grease chambeies; 4) be positioned at the initial position of travel switch 6 contacts on the piston rod according to situation such as landform, soil, weather adjustment, this contact position will be between profiling travel switch 6 and the following profiling travel switch 7, should be as far as possible near point midway; 5) after adjustment finished, all switches were in reset mode.
2. forming movement
When 1) going up profiling, piston rod shortens, and piston type gas-liquid accumulator 2 air chamber volumes reduce, and pressurize gas-liquid accumulator 8 is that piston type gas-liquid accumulator 2 grease chambeies replenish hydraulic oil.When 2) descending profiling, the piston rod elongation, piston type gas-liquid accumulator 2 air chamber volumes increase, and the hydraulic oil of piston type gas-liquid accumulator 2 grease chambeies is pressed in the pressurize gas-liquid accumulator 8.
3. go up profiling limit position
1) when profiling amount on the profiling parts 3 arrives maximum; Travel switch contact on the piston rod contacts with last profiling travel switch 6; The 5DT of 3-position-3-way solenoid directional control valve 9 energising at this moment; Other switch is in reset mode, and the pipeline between piston type gas-liquid accumulator 2 and pressurize gas-liquid accumulator 8 grease chambeies breaks off, and the hydraulic oil of piston type gas-liquid accumulator 2 grease chambeies is directly to oil cylinder 11 dischargings;
2) piston rod elongation; 3) when separate with last profiling travel switch 6 contact, the 5DT power-off restoration of 3-position-3-way solenoid directional control valve 9.
4. descend profiling limit position
1) when 3 times profiling amounts of profiling parts arrives maximum; Travel switch contact on the piston rod contacts with following profiling travel switch 7; The 1DT energising of normally closed type bi-bit bi-pass solenoid directional control valve 15 at this moment; Other switch is in reset mode, and grease chamber's hydraulic oil of auxiliary gas-liquid accumulator 5 is directly to oil cylinder 11 dischargings; 2) piston rod shortens; 3) when separate with following profiling travel switch 7 contact, the 1DT power-off restoration of normally closed type bi-bit bi-pass solenoid directional control valve 15.
5. when the profiling parts transport
1) A1 of manual adjustments 3-position 4-way solenoid directional control valve 10 or 3DT energising, other switch is in reset mode, and piston rod will shorten; 2) A3 of manual adjustments 3-position-3-way solenoid directional control valve 9 or 5DT energising, other switch is in reset mode, and piston rod will extend; 3) after the piston rod length adjustment finishes, the A2 of manual adjustments 3-position-3-way solenoid directional control valve 9 or 4DT energising, other switch is in reset mode, and this moment, piston rod was in locking state.
The stable problem of transportation that the associating implement structure is compact in order to solve, profiling one is made peace; The present invention provides a kind of compact conformation, the hinged feeler mechanism of good, easy to adjust, the adaptable double freedom list of profiling performance; This mechanism is the basis singly to be articulated and connected, be execution unit with gas-liquid accumulation of energy cylinder, and is auxiliary with hydraulic control system; When the upper and lower profiling of profiling workpiece that it connected; Moment with profiling elastic variable in the opposite direction can be provided, and be provided with upper and lower profiling extreme position, thereby guarantee to stablize profiling; This mechanism is lockable pistons work position also, and double freedom mechanism is become the rigidity cam mechanism, is convenient to complete machine transportation and transfer.The present invention has compact conformation, good, easy to adjust, the adaptable characteristics of profiling performance.
The invention has the beneficial effects as follows that this mechanism structure is compact, profiling is controlled, easy to adjust, adaptability is strong, automaticity is high, can realize Long-distance Control, helps designing and developing of agricultural machinery product.
Description of drawings
Fig. 1 is the structural representation of the hinged feeler mechanism of double freedom list
Fig. 2 is the hydraulic system sketch map of the hinged feeler mechanism of double freedom list
Including: 1. Front frame 2. Piston type gas-liquid accumulator 3. Profiling member 4. Single hinge point 5. Auxiliary liquid accumulator 6. Trip switch on profiling 7 8 next trip switch Profiling Holding pressure liquid accumulator 9 three-way solenoid valve 10. three-way solenoid valve 11. cylinder 12. pump 13a. pressure relief valve I? 13b. pressure relief valve II13c. Pressure relief valve III? 14a. way valve I? 14b. way valve II? 14c. way valve III 15. normally closed two two-way solenoid valve 16a. adjustable throttle I 16b. adjustable throttle II 16c. adjustable throttle III - the gas chamber on the piston rod of the force vector; - oil chamber on the piston rod of the force vector; - resistance, friction, traction, support force, gravity and other forces The combined force vector; 1DT-control normally closed two two-way solenoid valve solenoid; 2DT-controlled three-way solenoid valve solenoid side location; 3DT-controlled three-way electromagnetic transducer position to the other side of the solenoid valve; 4DT-controlled three-way solenoid valve side of the position of the electromagnet; 5DT-controlled three-way solenoid valve position of the other side of the electromagnet; A1-control three-way solenoid valve manual switch; A2-controlled three-way solenoid valve side of the position of the manual switch; A3-controlled three-way solenoid valve manual switch on the other side of the position; B - the front of the rack with liquid accumulator piston hinge point; C-front frame hinge point and profile parts; E-liquid accumulator piston and profile parts hinge point.
Embodiment
The present invention is made up of single pin joint 4, series connection gas-liquid accumulator group, hydraulic pump 12, hydraulic control system and auxiliary hydraulic pressure element; Wherein single pin joint 4 links together through hinged anterior frame 1 and profiling parts 3 with the piston type gas-liquid accumulator 2 of series connection gas-liquid accumulator group; When profiling parts 3 under external force when single pin joint 4 is done forming movement; The piston rod of piston type gas-liquid accumulator 2 is done corresponding stretching motion; Change air chamber and grease chamber's volume, produce corresponding power simultaneously and change, rebulid the dynamic balance of feeler mechanism; When profiling amount overshoot value, change dynamic balance through hydraulic control system and series connection gas-liquid accumulator group, change the flexible direction of piston rod, thereby change profiling trend; Piston rod may be locked on the fixed position, makes double freedom mechanism change the rigidity cam mechanism into, is convenient to the transportation and the transfer of profiling parts 3.
Series connection gas-liquid accumulator group: form by piston type gas-liquid accumulator 2, auxiliary gas-liquid accumulator 5 and pressurize gas-liquid accumulator 8; Wherein piston type gas-liquid accumulator 2 is execution work parts of this feeler mechanism; Air chamber one end and anterior frame 1 are hinged, and piston rod one end and the profiling parts 3 of piston type gas-liquid accumulator 2 are hinged; Auxiliary gas-liquid accumulator 5 is back work parts with pressurize gas-liquid accumulator 8; Be used for adjusting the pressure of piston type gas-liquid accumulator 2 air chambers and grease chamber; Air chamber one end of auxiliary gas-liquid accumulator 5 is connected through the air chamber of pneumatic circuit with piston type gas-liquid accumulator 2; Grease chamber's one end of auxiliary gas-liquid accumulator 5 is connected with hydraulic control system, and during work, the air chamber pressure of piston type gas-liquid accumulator 2 can kept or adjust to auxiliary gas-liquid accumulator 5; The air chamber one end sealing of pressurize gas-liquid accumulator 8; Grease chamber's one end of pressurize gas-liquid accumulator 8 is connected with grease chamber's one end of piston type gas-liquid accumulator 2 through hydraulic control component; During work, pressurize gas-liquid accumulator 8 guarantees the slow steady change of piston type gas-liquid accumulator 2 grease chamber's pressure.
Hydraulic control system: form by normally closed type bi-bit bi-pass solenoid directional control valve 15,3-position-3-way solenoid directional control valve 9,3-position 4-way solenoid directional control valve 10, last profiling travel switch 6 and following profiling travel switch 7 by hydraulic control system; Wherein normally closed type bi-bit bi-pass solenoid directional control valve 15 oil-ins are connected with the grease chamber of the auxiliary gas-liquid accumulator 5 of series connection gas-liquid accumulator group with adjustable throttling I 16a through the Pressure relief valve I of auxiliary hydraulic pressure element 13a, and oil-out is connected with oil cylinder 11; The oil-in of 3-position-3-way solenoid directional control valve 9 is connected with the grease chamber of the piston type gas-liquid accumulator 2 of series connection gas-liquid accumulator group with adjustable throttling II 16b through the Pressure relief valve II of auxiliary hydraulic pressure element 13b; First oil-out is connected with oil cylinder 11, the pressurize gas-liquid accumulator 8 of second oil-out and the gas-liquid accumulator group of connecting; The oil-in of 3-position 4-way solenoid directional control valve 10 is connected with hydraulic pump 12 through adjustable throttling III16c, Pressure relief valve III13c and the check valve III14c of auxiliary hydraulic pressure element; First oil-out is connected with oil cylinder 11; Second oil-out is connected with the grease chamber of the auxiliary gas-liquid accumulator 5 of series connection gas-liquid accumulator group through the check valve I of auxiliary hydraulic pressure element 14a, Pressure relief valve I 13a and adjustable throttling I 16a, and the 3rd oil-out is connected with piston type gas-liquid accumulator 2 grease chambeies of series connection gas-liquid accumulator group through check valve II14b, Pressure relief valve II 13b and the adjustable throttling II 16b of auxiliary hydraulic pressure element; Last profiling travel switch 6 places piston type gas-liquid accumulator 2 piston rods one end with following profiling travel switch 7; Grease chamber's decompression operation of the auxiliary gas-liquid accumulator 5 of normally closed type bi-bit bi-pass solenoid directional control valve 15 controls; The break-make of 3-position-3-way solenoid directional control valve 9 control pressurize gas-liquid accumulators 8 grease chambeies and the decompression operation of control piston formula gas-liquid accumulator 2 grease chambeies; 3-position 4-way solenoid directional control valve 10 control piston formula gas-liquid accumulators 2 grease chamber's fuel feeding, grease chamber's fuel feeding of the auxiliary gas-liquid accumulator 5 of control, hydraulic pump 12 fuel feeding are cut off in control; Last profiling travel switch 6, the logical triggering of profiling travel switch 7 controls each solenoid directional control valve when profiling reaches the limit of down.
Auxiliary hydraulic pressure element: form by Pressure relief valve I 13a, Pressure relief valve II 13b, Pressure relief valve III13c, check valve I 14a, check valve II 14b, check valve III14c, adjustable throttling I 16a, adjustable throttling II 16b and adjustable throttling III16c; Wherein Pressure relief valve I 13a places between check valve I 14a and the adjustable throttling I 16a; Pressure relief valve II 13b places between check valve II 14b and the adjustable throttling II 16b, and Pressure relief valve III13c places between check valve III14c and the adjustable throttling III16c; The auxiliary hydraulic pressure element is to be used for guaranteeing the stable and necessary parts of safety of hydraulic system.Check valve I 14a, check valve II 14b and check valve III14c are used for making oil stream to pass through from a direction, and can not reverse flow; Adjustable throttling I 16a, adjustable throttling II 16b and adjustable throttling III16c are the flows of controlling fluid through the size that changes restriction, to change the speed of executive component; Pressure relief valve I 13a, Pressure relief valve II 13b and Pressure relief valve III13c are used for guaranteeing the constant and security of system of fluid pressure line internal pressure.
Forming movement: when this feeler mechanism work; On the piston rod of piston type gas-liquid accumulator 2, there is a mechanical balance; Promptly wherein be the vectorial force of air chamber to piston rod; is the vectorial force of grease chamber to piston rod; is the resultant vector power of external force such as resistance, frictional force, tractive force, support force, gravity, and this mechanical balance guarantees that the corresponding piston rod stroke of a certain profiling amount is a definite value; Change as ; When profiling parts 3 are done to go up forming movement; Piston rod shortens; In reaching the process of balance position; The direction of and is in the opposite direction; In the opposite direction with ; Owing to there is pressurize gas-liquid accumulator 8; The value of steadily reduces; Along with piston type gas-liquid accumulator 2 air chamber volumes constantly dwindle; The value of constantly increases; Piston rod slowly shrinks, and profiling this moment parts 3 are made mild last forming movement; Change as ; When profiling parts 3 make forming movement; The piston rod elongation; In reaching the process of balance position; The direction of is identical with the direction of ; In the opposite direction with ; Owing to there is pressurize gas-liquid accumulator 8; The value of steadily strengthens; Along with piston type gas-liquid accumulator 2 air chamber volumes continue to increase; The value of constantly reduces; Piston rod slowly extends, and profiling this moment parts 3 are made mild following forming movement.
Change profiling trend: when profiling amount on the profiling parts 3 arrives maximum; If piston rod continues to shrink again; With the operation quality that influences profiling parts 3; Make grease chamber's emptying of piston type gas-liquid accumulator 2 at this moment through hydraulic control system, the value of reduces rapidly, thereby changes the mechanical balance of piston rod; Piston rod is extended fast, profiling parts 3 this position by on forming movement become down forming movement; When profiling amount under the profiling parts arrives maximum; If piston rod continues elongation again; With the operation quality that influences profiling parts 3; Make grease chamber's emptying of auxiliary gas-liquid accumulator 5 this moment through hydraulic control system; The air chamber volume of piston type gas-liquid accumulator 2 will strengthen rapidly, and the value of reduces rapidly, thereby change the mechanical balance of piston rod; Piston rod is shortened fast, and profiling parts 3 are forming movement on this position is become by following forming movement; After the profiling amount is got back to range of normal value, the state when hydraulic control system comes back to normal profiling.
Rigidity triangle bindiny mechanism: when profiling parts 3 need transportation; The oiling or the emptying of the grease chamber through hydraulic control system control piston formula gas-liquid accumulator 2; Thereby the length of adjustment piston rod makes profiling parts 3 arrive suitable transporting position, then the length through locked each fluid pressure line fixed piston rod; At the invariant position of when transportation 3 of B, C, E, so singly hinged double freedom feeler mechanism is transformed into rigidity triangle bindiny mechanism.

Claims (4)

1. hinged feeler mechanism of double freedom list; It is characterized in that forming by single pin joint (4), series connection gas-liquid accumulator group, hydraulic pump (12), hydraulic control system and auxiliary hydraulic pressure element; Its middle front part frame (1) links together with profiling parts (3) through the piston type gas-liquid accumulator (2) of single pin joint (4) and series connection gas-liquid accumulator group, and piston rod one end of piston type gas-liquid accumulator (2) is equipped with the last profiling travel switch (6) and the following profiling travel switch (7) of hydraulic control system; Normally closed type bi-bit bi-pass solenoid directional control valve (15) oil-in of hydraulic control system is connected with auxiliary gas-liquid accumulator (5) grease chamber of adjustable throttling I (16a) with series connection gas-liquid accumulator group through auxiliary hydraulic pressure element Pressure relief valve I (13a); 3-position-3-way solenoid directional control valve (9) oil-in of hydraulic control system is connected with piston type gas-liquid accumulator (2) grease chamber of adjustable throttling II (16b) with series connection gas-liquid accumulator group through auxiliary hydraulic pressure element Pressure relief valve II (13b); 3-position 4-way solenoid directional control valve (10) oil-in of hydraulic control system is connected with hydraulic pump (12) through auxiliary hydraulic pressure element adjustable throttling III (16c), Pressure relief valve III (13c) and check valve III (14c); First oil-out is connected with oil cylinder (11); Second oil-out is connected with auxiliary gas-liquid accumulator (5) grease chamber of series connection gas-liquid accumulator group through check valve I (14a), Pressure relief valve I (13a) and the adjustable throttling I (16a) of auxiliary hydraulic pressure element, and the 3rd oil-out is connected through auxiliary hydraulic pressure element check valve II (14b), Pressure relief valve II (13b) and adjustable throttling II (16b) piston type gas-liquid accumulator (2) grease chamber with series connection gas-liquid accumulator group.
2. by the hinged feeler mechanism of the described double freedom list of claim 1; It is characterized in that described series connection gas-liquid accumulator group is made up of piston type gas-liquid accumulator (2), auxiliary gas-liquid accumulator (5) and pressurize gas-liquid accumulator (8); Wherein air chamber one end of piston type gas-liquid accumulator (2) and anterior frame (1) are hinged, and piston rod one end and the profiling parts (3) of piston type gas-liquid accumulator (2) are hinged; Air chamber one end of auxiliary gas-liquid accumulator (5) is connected through the air chamber of pneumatic circuit with piston type gas-liquid accumulator (2), and grease chamber's one end of auxiliary gas-liquid accumulator (5) is connected with hydraulic control system; The air chamber one end sealing of pressurize gas-liquid accumulator (8), grease chamber's one end of pressurize gas-liquid accumulator (8) is connected with grease chamber's one end of piston type gas-liquid accumulator (2) through hydraulic control component.
3. by the hinged feeler mechanism of the described double freedom list of claim 1; It is characterized in that described hydraulic control system by normally closed type bi-bit bi-pass solenoid directional control valve (15), 3-position-3-way solenoid directional control valve (9), 3-position 4-way solenoid directional control valve (10), go up profiling travel switch (6) and following profiling travel switch (7) is formed; Wherein normally closed type bi-bit bi-pass solenoid directional control valve (15) oil-in is connected with auxiliary gas-liquid accumulator (5) grease chamber of adjustable throttling I (16a) with series connection gas-liquid accumulator group through the Pressure relief valve I (13a) of auxiliary hydraulic pressure element, and oil-out is connected with oil cylinder (11); 3-position-3-way solenoid directional control valve (9) oil-in is connected with the grease chamber of adjustable throttling II (16b) with the piston type gas-liquid accumulator (2) of series connection gas-liquid accumulator group through the Pressure relief valve II (13b) of auxiliary hydraulic pressure element; First oil-out is connected with oil cylinder (11), and second oil-out is connected with the grease chamber of the pressurize gas-liquid accumulator (8) of series connection gas-liquid accumulator group; 3-position 4-way solenoid directional control valve (10) oil-in is connected with hydraulic pump (12) through adjustable throttling III (16c), Pressure relief valve III (13c) and the check valve III (14c) of auxiliary hydraulic pressure element; First oil-out is connected with oil cylinder (11); Second oil-out is connected with auxiliary gas-liquid accumulator (5) grease chamber of series connection gas-liquid accumulator group through check valve I (14a), Pressure relief valve I (13a) and the adjustable throttling I (16a) of auxiliary hydraulic pressure element, and the 3rd oil-out is connected with piston type gas-liquid accumulator (2) grease chamber of series connection gas-liquid accumulator group through check valve II (14b), Pressure relief valve II (13b) and the adjustable throttling II (16b) of auxiliary hydraulic pressure element; Last profiling travel switch (6) and following profiling travel switch (7) place piston type gas-liquid accumulator (2) piston rod one end.
4. by the hinged feeler mechanism of the described double freedom list of claim 1; It is characterized in that described auxiliary hydraulic pressure element is made up of Pressure relief valve I (13a), Pressure relief valve II (13b), Pressure relief valve III (13c), check valve I (14a), check valve II (14b), check valve III (14c), adjustable throttling I (16a), adjustable throttling II (16b) and adjustable throttling III (16c); Wherein Pressure relief valve I (13a) places between check valve I (14a) and the adjustable throttling I (16a); Pressure relief valve II (13b) places between check valve II (14b) and the adjustable throttling II (16b), and Pressure relief valve III (13c) places between check valve III (14c) and the adjustable throttling III (16c).
CN2010102353739A 2010-07-18 2010-07-18 Two-degree-of-freedom single hinged profiling mechanism Expired - Fee Related CN101940092B (en)

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JP5513535B2 (en) * 2012-01-25 2014-06-04 カヤバ工業株式会社 Circuit pressure control device, hydraulic control circuit using this circuit pressure control device, and hydraulic control circuit for construction machine
CN112314092A (en) * 2020-12-04 2021-02-05 浙江星莱和农业装备有限公司 Multifunctional agricultural mechanical structure

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